TABLES  AND  DIAGRAMS 


RELATING  TO 


NON-CONDENSING 


ENGINES  &  BOILERS 


W.    P.    TROWBRIDGE. 


YORK: 
J  O  H  ]Sr     WILEY    &     SON, 

15     ASTOR     PLACE. 

1872. 


rsr 


ENTERED     ACCORDING     TO     ACT     OF    CONGRESS,     IN     THE     YEAR     1872, 

BY 

JOHN     WILEY     &    SON, 

IN  THE  OFFICE  OF  THE  LIBRARIAN  OF  CONGRESS,  AT  WASHINGTON. 


INTRODUCTORY     NOTE. 


Tins  collection  of  tables  for  non-condensing  engines  and  boilers,  and  also  the  explanations  relating  to 
them,  including  those  which  refer  to  Horse  Power  of  Engines,  and  the  Diagrams  showing  the  quantity  of 
water  required  per  horse  power  per  hour  for  different  degrees  of  expansion,  was  originally  prepared  at  the 
Novelty  Iron  Works,  New  York,  as  a  basis  for  the  manufacture  and  sale  of  engines. 

The  explanatory  note  relating  to  the  Horse  Power  of  Engines  was  prepared  by  Mr.  Horatio  Allen, 
President  of  the  Novelty  Iron  Works. 

The  explanations  in  regard  to  the  tables  of  engines  and  boilers  were  prepared  by  Mr.  0.  E.  Emery, 
who  made,  for  the  Novelty  Iron  Works,  the  valuable  experiments  which  formed  the  basis  of  the  tables. 

The  description  of  the  manner  in  which  the  experiments  were  conducted  is  given  by  Mr.  Emery,  in  a 
note  accompanying  the  diagrams ;  and  the  computations  of  the  tables  were  also  made  by  him. 

It  was  intended  to  publish  the  results  of  the  experiments  and  the  resulting  tables  in  connection  with 
the  sale  of  engines,  but  the  resolution  of  the  proprietors  of  the  Novelty  Iron  Works  to  close  the  works,  made 
it  necessary  to  withhold  the  matter  from  publication,  notwithstanding  it  had  been  put  into  printed  form. 

Believing  that  the  information  obtained  and  set  forth  in  a  manner  so  readily  comprehended  and 
applicable,  may  be  valuable  for  reference  fc>  all  who  wish  to  manufacture  or  employ  the  non-condensing  steam 
engine,  I  procured  the  matter  already  printed,  with  a  view  of  publishing  it  in  the  form  in  which  it  is  here 
presented. 

This  explanation  is  rendered  necessary  on  account  of  the  references  to  the  Novelty  Iron  Works  which 
occur  in  the  headings,  and  in  other  parts  of  the  text. 

I  have  added  notes  and  tables  on  the  horse  powers  of  boilers,  and  on  boiler-explosions  and  safety 
valves,  subjects  connected  practically  with  the  manufacture  and  management  of  boilers,  but  which  were  not 
included  in  the  original  design  of  the  publication  by  the  Novelty  Iron  Works. 

The  practical  value  of  this  extended  list  of  engines  and  boilers  to  those  who  wish  to  purchase  or 
manufacture  engines  for  special  purposes  consists  in  this,  that  for  a  range  of  5  to  300  horse  power,  a  choice 
is  offered  of  various  dimensions  of  engines,  speeds  of  revolution  and  pressures  of  steam ;  and  for  each  engine 
in  the  list,  the  quantity  of  water,  or  steam,  per  hour  which  this  engine  will  require  is  given.  The  list  of 
boilers,  on  the  other  hand,  furnishes  the  means  of  selecting  the  boiler  or  boilers  of  the  principal  types 
necessary  to  produce  this  steam. 

Moreover,  the  diagrams  showing  the  expenditure  of  steam  or  water  per  horse  power  per  hour,  for  any 
degree  of  expansion  in  any  particular  engine  with  a  given  pressure,  furnish  a  ready  means  of  comparing 
the  performance  of  such  engine  with  a  perfect  standard. 

The  question  of  the  limit  of  economy  of  expansion  is  here  thoroughly  and  practically  settled ;  and 
the  results,  as  was  to  be  anticipated,  confirm  the  deductions  of  theory. 

The  tables  possess,  therefore,  a  special  interest,  not  only  in  their  practical  applications,  but  also  in 
connection  with  corresponding  theoretical  deductions. 

W.  P.  TROWBRIDGE, 

Professor  of  Dynamic  Engineering. 
SHEFIELD  SCIENTIFIC  SCHOOL,  YALE  COLLEGE,  APRIL  5,  1872. 


mes. 


'HE  power  which  a  Steam  Engine  can  furnish  is  generally  expressed  in  "Horse  Power."     It  will 

therefore  be  of  interest  to  most  purchasers,  and  of  special  value  to  many,  to  have  briefly  stated, 

what  is  meant  by  a  "  Horse  Power,"  and  how  it  has  happened  that  the  power  of  a  Steam  Engine 
is  thus  expressed  in  reference  to  that  of  Horses. 

Prior  to  the  introduction  of  the  Steam  Engine,  horses  were  very  generally  used  to  furnish 
power  to  perform  various  kinds  of  work,  and  especial!}-  the  work  of  pumping  water  out  of  mines, 
raising  coal,  etc.  For  such  purposes  several  horses  working  together  were  required.  Thus,  to  work 
the  pumps  of  a  certain  mine,  five,  six,  seven  or  some  other  number  of  horses  were  found  necessary. 
When  it  was  proposed  to  substitute  the  new  power  of  steam,  the  proposal  naturally  took  the  form  of 
furnishing  a  Steam  Engine  capable  of  doing  the  work  of  the  number  of  horses  used  at  the  same  time. 
Hence,  naturally  followed  the  usage  of  stating  the  number  of  horses  which  a  particular  engine  was 
equal  to,  that  is,  its  "Horse  Power." 

But  as  the  two  powers  were  only  alike  in  their  equal  capacity  to  do  the  same  work  it  became 
necessary  to  refer  in  both  powers  to  some  work  of  a  similar  character  which  could  be  made  the  basis  of 
comparison.  Of  this  character  was  the  work  of  raising  a  weight  perpendicularly. 

A  certain  number  of  horses  could  raise  a  certain  weight,  as  of  coal,  out  of  a  coal  mine,  at  a 
certain  speed  ;  a  Steam  Engine,  of  certain  dimensions  and  supply  of  steam,  could  raise  the  same 
weight  at  the  same  speed.  Thus,  the  weight  raised  at  a  known  speed  could  be  made  the  common 
measure  of  the  two  powers.  To  use  this  common  measure  it  was  necessary  to  know  what  was  the 
power  of  one  horse  in  raising  a  weight  at  a  known  speed. 

By  observation  and  experiment  it  was  ascertained  that,  referring  to  the  average  of  horses,  the 
most  advantageous  speed  for  work  was  at  the  rate  of  two-and-a-half  miles  per  hour — that,  at  that  rate, 
he  could  work  eight  hours  per  day  raising,  perpendicularly,  from  100  to  150  ftis.  The  higher  of  these 
weights  was  taken  by  Watt,  that  is,  150  fts.  at  2J  miles  per  hour.  But  this  fact  can  be  expressed  in 
another  form:  2£  miles  per  hour  is  220  feet  per  minute  (^fjp'  = 220)-  So,  the  power  of  a  horse  was 
taken  at  150  ibs.,  raised  perpendicularly,  at  the  rate  of  220  feet  per  minute.  This  also  can  be  expressed 
in  another  form :  The  same  power  which  will  raise  150  fos.  220  feet  high  each  minute,  will  raise 

300  fts.  110  feet  high  each  minute. 
3,000  fts.     11         " 
33,000  ft>s.       1         "  " 

For  in  each  case  the  total  work  done  is  the  same,  viz. :  same  number  of  pounds  raised  one  foot  in 
one  minute. 

If  it  is  clearly  perceived  that  33,000  fts.,  raised  at  the  rate  of  one  foot  high  in  a  minute,  is  the 
equivalent  of  150  fts.,  at  the  rate  of  220  feet  per  minute  (or  2£  miles  per  hour),  it  will  be  fully 
understood  how  it  is  that  33,000  tbs.,  raised  at  the  rate  of  one  foot  per  minute  expresses  the  power  of 
one  horse,  and  has  been  taken  as  the  standard  measure  of  power. 


Horse    bovver    of   Steam.    Engines. 


It  has  thus  happened  that  the  mode  of  designating  the  power  of  a  Steam  Engine  has  been  by 
"Horse  Power,"  and  that  one  horse  power,  expressed  in  pounds  raised,  is  a  power  that  raises  33,000  fos. 
one  foot  each  minute.  This  unit  of  power  is  now  universally  received.  Having  a  Horse  Power 
expressed  in  pounds  raised,  it  was  easy  to  state  the  power  of  a  Steam  Engine  in  Horse  Power,  which 
was  done  in  the  following  manner: 

The  force  with  which  steam  acts  is  usually  expressed  in  its  pressure  in  pounds  on  each  square 
inch.  The  Piston  of  a  High  Pressure  Steam  Engine  is  under  the  action  of  the  pressure  of  steam  from 
the  boiler,  on  one  side  of  the  piston,  and  of  the  back  action  of  the  pressure  due  to  the  discharging 
steam,  on  the  other  side.  The  difference  between  the  two  pressures  is  the  effective  pressure  on  the 
piston,  and  the  power  developed  by  the  motion  of  the  piston,  under  this  pressure,  will  be  according  to 
the  number  of  square  inches  acted  on,  and  the  speed  per  minute  with  which  the  piston  is  assumed  to 
move.  Thus,  let  the  number  of  square  inches  in  surface  of  piston  of  a  steam  engine  be  100,  and  the 
effective  pressure  on  each  square  inch  be  33  Ibs.,  and  the  movement  of  piston  be  at  the  rate  of  200  feet 
per  minute,  then  the  total  effective  pressure  on  the  piston  will  be  100  x  33  =  3,300  fibs.,  and  the 
movement  being  200  feet  per  minute,  the  piston  will  move  with  a  power  equal  to  raising  660,000  fibs., 
one  foot  high  each  minute  (as  3,300  x  200  is  660,000),  and  as  each  33,000  fibs.,  raised  one  foot  high,  is  one 
horse  power  and  "/^oW0  is  20,  then  the  power  of  this  Engine  is  20  Horse  Power.  If  this  power  is  used 
to  do  work,  a  part  of  it  will  be  expended  in  overcoming  the  friction  of  the  parts  of  the  engine  and  of 
the  machinery  through  which  the  power  is  transmitted  to  perform  the  work.  The  calculation  made 
refers  to  the  total  power  developed  by  the  movement  of  the  piston  under  the  pressure  of  steam. 

The  number  of  feet  moved  by  the  piston  each  minute  is  known  from  the  length  of  stroke  of 
piston  in  feet,  and  number  of  revolutions  of  engine  per  minute,  there  being  two  strokes  of  the  piston 
for  each  revolution  of  the  engine.  When  these  three  facts  are  known  the  power  of  an  engine  can  be 
readily  and  accurately  ascertained,  and  it  is  evident  that,  without  the  knowledge  of  each  of  the  facts, 
viz. :  square  inches  of  piston,  effective  pressure  on  each  square  inch,  and  movement  of  piston  per 
minute,  the  power  cannot  be  known. 

But  circumstances,  especially  those  existing  when  the  Condensing  Engine  was  introduced  by 
Watt,  led  to  assumptions  as  to  pressure  per  square  inch  and  speed  of  piston,  which,  though  true  at  the 
time,  have  long  since  ceased  to  be  true,  and  consequently  the  rules  based  on  such  assumptions  are 
entirely  inapplicable,  and  when  used  must  of  necessity  give  false  statements.  As,  however,  such  rules 
are  still  in  use,  although  with  the  precautionary  and  unsatisfactory  designation  of  nominal  power,  it  is 
necessary  to  state  what  Nominal  Horse  Power  is.  In  the  United  States  the  designation  of  Nominal 
Horse  Power  for  Condensing  Engines  is  seldom  used,  but  in  England  the  usage  still  prevails. 

After  Watt  had  introduced  the  Condensing  Engine,  he  gave  convenient  rules  for  determining  the 
power  of  his  engines,  and  as,  at  that  time,  the  steam  pressure  and  piston  speed  in  general  use  were 
very  low,  his  rule  was  based  on  the  assumption  that,  in  all  steam  engines,  the  effective  pressure  was 
7  fibs,  per  square  inch,  and  that  the  speed  of  the  piston -varied  with  the  length  of  stroke  from  160  feet 
per  minute  for  2  feet  stroke  to  256  feet  per  minute  for  8  feet  stroke.  The  only  facts  necessary  to  obtain 
were  the  diameter  of  cylinder  and  length  of  stroke.  The  nominal  power  was  then  determined  by 
Watts'  rule,  which  is  as  follows : 

RULE. — Multiply  the  square  of  the  diameter  of  the  cylinder  in  inches  by  the  cube  root  of  the  stroke  in  feet, 
and  divide  the  product  by  47.  The  quotient  is  the  nominal  horse  power  of  the  Engine. 

For  many  years,  and  especially  in  the  United  States,  this  rule  has  ceased  to  be  of  any  value. 
This  becomes  plainly  the  case  when,  instead  of  7  fibs,  per  square  inch,  the  pressure  actually  used 
greatly  exceeds  7,  being  from  20  to  50  and  over,  while  the  speed  of  piston  is  often  from  400  to  700  feet 
per  minute. 


Horse    Power    of   Steam    Engines,    etc. 


Some  mocliliuations  of  *his  rule  have  been  made,  but  it  is  plain  that  when  the  pressure  of  steam 
and  speed  of  piston  are  so  various  as  at  present  it  is  simply  not  possible  to  have  a  general  rule.  If  it 
becomes  necessary  to  state  the  power  of  an  engine,  then  the  three  facts  named  above,  viz. :  number  of 
square  inches  of  piston,  effective  pressure  per  square  inch  per  stroke  of  piston,  and  speed  of  piston  must 
be  known  or  assumed,  and  when  known  or  assumed  the  Horse  Power  can  in  that  case  be  ascertained, 
as  explained  above. 

In  the  United  States,  it  is  still  usual  to  assign  a  certain  Horse  Power,  often  called  "Rated  Horse 
Power,"  for  High  Pressure  Engines  of  certain  dimensions,  thus  a  cylinder  of  12  inches  diameter,  3  feet 
stroke  is  often  called  20  horse  power,  and  so  of  other  dimensions. 

The  considerations  already  presented  show  that  it  is  plainly  impossible  to  say  what  horse  power 
a  12  inch  diameter,  3  feet  stroke  cylinder  is,  unless  there  is  also  stated  what  effective  pressure  on  the 
piston,  and  speed  of  piston  are  to  be  used. 

At  what  steam  pressure  that  Engine  will  be  used,  and  with  what  speed  of  piston  run,  remains  to 
be  decided,  and  until  they  are  decided  nothing  can  be  said  as  to  the  power  of  the  Engine.  As  it  would 
not  be  safe  to  subject  the  Engine  to  higher  steam  than  that  for  which  it  was  built,  nor  to  run  it  at 
higher  speed  than  it  is  known  its  moving  surface,  in  contact  will  bear,  the  maximum  capacity  of  an 
Engine  can  be  stated,  within  which  the  power  of  that  Engine  will  be  determined  by  the  pressure  and 
speed  actually  used. 


The  tables  commencing  at  page  7  show  "  The  sizes  of  the  Non- Condensing,  Stationary  Steam  Engines, 
built  at  the  Novelty  Iron  Works,  New  York ;  and  the  Revolutions,  Steam  Pressures  and  Points  of  Cut-off  which 
will  produce  the  several  Horse  Powers  named ;  also  the  Amount  of  Water  used  per  Hour  and  Cost  of  the  Power 
per  Year,  for  each  case." 

Non- Condensing  Engines,  or,  as  they  are  often  incorrectly  called,  High  Pressure  Engines,  are  those 
in  which  the  steam,  after  its  action  on  the  piston,  is  permitted  to  escape  into  the  atmosphere,  and  in 
which,  therefore,  the  pressure  of  the  outgoing  steam  must  exceed  the  atmospheric  pressure  of  fifteen 
pounds  to  the  square  inch. 

There  are  two  kinds  of  Horse  Power  referred  to  in  the  tables,  viz. :  The  Indicated  Horse  Power 
and  the  Net  Horse  Power.  The  Indicated  Horse  Power  is  obtained  by  multiplying  together  the  mean 
effective  pressure  in  the  cylinder,  in  pounds  per  square  inch,  the  area  of  the  piston  in  square  inches, 
and  the  speed  of  piston,  in  feet  per  minute,  and  dividing  the  product  by  33,000 ;  and  as  the  effective 
pressure  on  the  piston  is  measured  by  an  instrument  called  the  Indicator,  the  power  calculated 
therefrom  is  called  the  Indicated  Horse  Power.  The  Net  Horse  Power  is  the  power  available  for  useful 
work,  and  may  be  determined  by  subtracting,  from  the  Indicated  Horse  Power,  the  power  required  to 
overcome  the  friction  of  the  engine,  when  in  the  performance  of  its  regular  duty.  For  instance,  if  a 


6  Explanation    of  tlie    Tables. 

person  desires  an  engine  to  drive  ten  machines,  each  requiring  ten  Horse  Power,  the  engine  should  he 
of  sufficient  size  to  furnish  one  hundred  Net  Horse  Power ;  but  to  produce  this  would  require  about 
one  hundred  and  fifteen  Indicated  Horse  Power. 

We  manufacture  two  classes  of  engines,  designated  in  the  tables  as  "Long  Stroke  Engines"  and 
"•Short  Stroke  Engines."  These  engines,  as  suggested  by  their  names,  have  different  proportions  of 
stroke  to  diameter,  and  the  shorter  strokes  are  made  with  increased  size  of  brasses  and  other 
modifications  of  detail  which  fit  them  for  high  speeds. 

Column  A  of  the  tables  shows  the  "Net  Horse  Power"  which  has  been  calculated  for  the  various 
powers  usually  required  between  5  and  350  Horse  Power.  Each  Horse  Power  can  be  obtained  in  a 
variety  of  ways,  shown  by  the  adjacent  columns.  The  Net  Horse  Powers  shown  in  the  tables  were 
obtained  from  the  estiinated  Indicated  Horse  Powers,  by  deducting  liberal  allowances  for  friction.  In 
the  calculations,  it  was  assumed  that  the  short  stroke  engines  have  more  friction  than  the  long  stroke. 

Column  ii  shows  the  "Steam  Pressures"  above  the  atmosphere  assumed  for  each  case.  The 
calculations  have  been  made  for  pressures  of  60,  80  and  100  Ibs.,  as  being  those  in  most  general  use,  in 
non-condensing  engines. 

Column  c  shows  the  "Point  of  Cut-off"  for  each  case.  The  table  gives  the  results  when  the  steam 
is  cut  oft'  at  |,  £  and  f  of  the  stroke  from  the  beginning,  which  means  that  the  full  pressure  of  the 
steam  has  been  allowed  to  act  on  the  piston  during  ^,  J  or  J  of  the  stroke,  and  that  the  remainder  of 
the  stroke,  in  each  case,  has  been  completed  b}"  the  expansion  of  the  steam. 

Column  D,  in  each  class  of  engine,  shows  the  "Size  and  Designation"  of  the  engine.  For 
instance,  the  expression  5  x  12  means  that  the  piston  is  five  inches  in  diameter  and  twelve  inches  stroke, 
and  that  the  engine  is  designated  or  called  a  U5  by  12  Engine,"  instead  of  a  five  Horse  Power 
Engine,  for  reasons  before  stated. 

Column  E  shows,  for  each  class  of  engine,  the  "Revolutions  per  Minute"  at  which  the  several 
engines  must  be  run,  in  order  to  produce  the  Net  Horse  Powers  named,  at  the  steam  pressures  and 
points  of  cut-off  shown. 

Columns  F  and  F  show  the  number  of  pounds  of  "  Water,"  evaporated  into  steam,  required 
"per  Indicated  Horse  Power  per  hour,"  for  each  case.  The  facts  were  obtained  from  experiments  which 
are  hereinafter  explained  and  illustrated.  This  column  shows  the  comparative  economy  of  the  different 
methods  of  producing  the  power,  and  from  it  may  readily  be  calculated  the  amount  of  coal  required 
per  Indicated  Horse  Power  per  hour. 

Columns  «  and  u  show  the  "  Total  Amount  of  Water  per  hour,"  in  pounds,  necessary  to  be 
evaporated  to  produce  the  Net  Horse  Power  named.  The  results  are  calculated  from  the  quantities  in 
line  F,  due  allowance  being  made  for  the  difference  between  the  Indicated  and  Net  Horse  Power. 
This  column  shows  the  evaporative  power  of  the  boiler  required  for  each  case. 

Columns  n  and  i  show,  for  each  class  of  engine,  the  "Cost  per  Year  of  the  Net  Horse  Power 
named."  Column  n  shows  the  cost  of  the  coal  for  one  year,  on  the  supposition  that  the  engine  runs 
ten  hours  per  day,  for  300  days  in  the  year;  that  the  coal,  including  cost  of  handling,  etc.,  costs  $8.00 
per  ton  of  2,000  Ibs.,  and  that  each  pound  of  coal  evaporates  eight  pounds  of  water.  Variations  may 
be  made,  by  simple  calculations,  when  the  price  of  coal  or  the  evaporation  differs  from  the  assumption. 
The  quantities  in  column  i  were  obtained  by  adding  to  the  cost  of  the  coal,  in  each  case,  the  interest  at 
ten  per  cent,  on  the  estimated  cost  of  the  engine.  This  column  shows,  then,  the  total  cost  of  the 
power  per  year  for  fuel  and  interest. 


Explanation    of  the    Tables.  6" 


These  tables  and  diagrams  are  based  chiefly  on  experiments  made  for  the  Novelty  Iron  Works,  under 
the  direction  of  Mr.  Charles  E.  Emery,  formerly  of  the  U.  S.  Naval  Engineers,  with  machinery  constructed 
especially  for  the  purpose.  Confirmatory  results  were,  however,  derived  from  the  previous  practice  of  that 
and  other  establishments,  and  from  experiments  made  for  the  U.  S.  Navy,  and  under  Government 
Commissioners.  It  had  been  shown  conclusively  that  the  attempt  to  make  a  complete  series  of  experiments, 
under  the  many  changes  of  condition  necessary  to  a  complete  investigation,  with  large  engines  involved  an 
incredible  amount  of  labor  and  expense,  and  would  occupy  a  period  of  time  almost  prescriptive.  It  was 
found,  however,  that  by  exercising  care  in  the  construction  and  operation  of  a  small  engine  the  results  would 
show  the  laws  applicable  to  engines  of  all  sizes,  and  the  apparatus  could  be  at  all  times  under  the  direction  of 
the  same  persons,  and  thus  secure  great  uniformity  of  observation. 

The  steam  cylinder  of  the  engine  constructed  for  the  experiments  referred  to  herein  was  eight  inches 
in  diameter,  and  had  eight  inches  stroke  of  piston.  The  power  was  applied  to  give  motion  to  a  lar»-e  fan- 
blowei,  the  speed  of  the  engine  being  regulated  by  a  gate  in  the  discharge  orifice  of  the  blow-er.  Steam  was 
supplied  from  a  locomotive  boiler  with  a  high  steam  drum,  and  the  steam  pipes  and  cylinders  were  carefully 
fitted.  The  bed  plate  of  the  cylinder  formed  a  surface  condenser,  to  which  was  connected  an  efficient  air- 
pump  operated  from  the  engine  crosshead.  The  cylinder  ports  were  of  ample  area,  and  the  cut-off  was 
performed  by  plates  having  a  9-inch  movement  over  the  back  of  the  main  valve.  The  Power  was  measured 
with  a  Richards'  Steam  Engine  Indicator,  used  in  connection  with  a  clock  and  engine  register. 

The  cost  of  the  Power  was  ascertained  by  weighing  the  amount  of  water  (condensed  steam)  delivered 
from  the  air  pump.  The  valves  and  piston  of  the  engine  were  by  good  workmanship  and  extended  operation 
made  perfectly  tight,  under  the  maximum  pressure  used,  and  examinations  were  frequently  made  to  prevent 
the  possibility  of  steam  or  water  leaks.  During  the  experiments  herein  referred  to  air  was  let  into  the 
condenser  to  destroy  the  vacuum. 

During  each  experiment  the  steam  pressure  and  revolutions  were  kept  exactly  uniform.  Each 
experiment  was  started  with  everything  in  average  working  condition — the  engine  register  being  thrown  in 
gear,  and  the  vessel,  to  receive  the  water  from  the  hot  well,  pushed  under  the  delivery  of  the  latter 
simultaneously,  at  an  even  minute,  as  shown  by  the  second-hand  of  the  clock.  Exactly  at  the  end  of  every 
hour,  to  the  second,  the  position  of  the  engine  register  was  noted,  the  water  vessels  shifted,  and  the  one 
removed  weighed  on  a  platform  scale. 

This  method  of  working  insured  such  remarkable  correspondence  in  the  results  that  it  was  found 
possible  to  reduce  the  duration  of  many  of  the  experiments  to  a  single  hour  each.  After  each  experiment 
some  condition, — for  instance,  the  point  of  cut-off, — was  slightly  changed,  and  another  experiment  started 
immediately  after.  This  operation  was  continued,  and  the  power  and  its  cost  calculated  for  each  instance, 
when  the  results  were  dotted  in  proper  position  on  a  ruled  sheet,  and  with  the  points  as  a  guide,  curves  were 
drawn  similar  to  those  shown  on  page  23.  In  this  way  the  modification  of  result  due  to  changing  the  three 
first  conditions  mentioned  on  page  24  were  obtained,  viz.,  1st,  "  The  steam  pressure ;"  2d,  "  The  amount  of 
expansion ; "  and  3d,  "  The  speed  of  revolution."  The  modification  due  to — 4th — "  The  size  of  cylinders," 
was  approximated  by  comparing  the  results  with  those  obtained  from  larger  engines  operated  under  similar 
conditions.  The  experimental  results  were  checked  again  by  calculating  theoretical  curves  similar  to  G  and 
H,  page  23,  for  each  steam  pressure,  in  which  all  the  conditions,  including  an  allowance  for  the  condensation 
due  to  the  mechanical  work  done,  were  taken  into  consideration.  All  the  results  are  in  harmony,  and  furnish 
a  reliable  basis  for  the  information  herein  contained. 

The  tables  are  not  designed  to  show  the  maximum  result  possible  under  the  conditions  named,  but 
such  as  should  be  expected  in  ordinary  good  practice. 

The  proper  size  of  boiler  of  either  of  the  different  types  mentioned  required  to  evaporate  a  given 
quantity  of  water  was  determined  in  tl^e  different  ways  by  different  individuals — one  collating  the  previous 
practice  of  the  Novelty  Iron  Works  and  other  establishments  ;  the  other  comparing  numerous  experiments  on 
the  subject.  The  results  agreed  in  a  most  satisfactory  manner.  The  tables  on  this  subject  were,  however, 
calculated  witli  considerable  allowance  for  difference  in  condition,  fuel,  and  management ;  the  necessity  of 
which  allowance  will  be  appreciated  by  the  practical  engineer. 


TABLES 

SHOWING    THE    SIZES    OF 

THE    NON-CONDENSING 

H 

iu*I 

f  gti 

1 

IN 

O'i 

BO 

% 

BUILT    AT 

THE  NOVELTY  IRON  WORKS, 

NEW  YORK; 

AND     THE 

Revolutions, 

Si 

I 

Presswi 

m 

i 

'oinis 

of 

iml- 

off, 

WHICH    WILL    PRODUCE   THE 

SEVERAL 

HORSE    POWERS    ISTAMED  ; 

ALSO   THE 

AMOUNT  OF  WATER  USED  PER  HOUR  AND  COST 

OF 

THE  POWER 

PER  YEAR, 

FOR    EACH 

CASE. 

STEAM 

LONG     STROKE     ENGINES 

SHORT     STROKE     ENGINES 

ENGINE 

WATER 

COST  PER  YEAR 

OP  THE    POWER  NAMED 

ENGINE 

WATER 

COST  PER  YEAR 
OP  THE   POWER  NAMED 

A 

B               C 

L>                      E 

F 

o 

H 

i 

D 

E 

F 

a 

H 

i 

NET 
HORSE 
POWER 

Pressure  above  At 
mosphere  in  pounds 
per  square  inch 

i  o  I 

Si  *  * 

Size  and 
Designa 
tion 

Revolutions  per 
Minute 

Per 
I.  H.  P. 
per 

Hour 

TOTAL 
Per  Hour 
for  Net 
Horse 
Power 
named 

For  Coal 
at  $8.00 
per  Ton 

TOTAL, 

(Interest 
on  cost  of 
Engine 
included) 

Size  and 
Designa 
tion 

Revolutions  per 
Minute 

Per 
I.  H.  P. 

per 
Hour 

TOTAL 
Per  Hour 
for  Net 
Horse 
Power 
named 

For  Coal 
at  $8.00 
per  Ton 

TOTAL, 

(Interest 
on  cost  of 
Engine 
included) 

d 

I 

9 

S 

15 

s 

1 

In. 

In. 

Lbs. 

Lbs. 

In. 

In, 

Lbs. 

Lbs. 

5 

100    1  stroke 
100    i  " 

5x12 
6x16 

95 

50 

30.4 
32.9 

190 
206 

$285 
309 

$375 
409 

!   5x    9 
6x    9 

129 

90 

28.9 

30.3 

183 

192 

$275 
288 

$343 
363 

H.  P. 

80    i  " 
80    i  " 

5x12 
6  x  16 

123 

64 

31.4 
34.4 

196 
215 

294 
323 

384 
423 

5x    9 
6x   9 

167 
116 

30.0 
31.5 

190 
199 

285 
299 

353 
374 

60    i  " 

5x12 

173 

33.3 

209 

314 

404 

5x    9 

235 

31.6 

200 

300 

368 

60    i  " 
60    i  " 

6x16 

7x20 

91 
53 

36.6 
39.3 

216 
243 

324 
365 

424 
475 

!   6x    9 
7x12 

163 

89 

33.2 
36.2 

210 

226 

315 
339 

390 
422 

100    |,troke 

5x12 

65 

37.6 

235 

$353 

$443 

1   5x   9| 

87 

35.9 

227 

$341 

$409 

80    i  " 

5x12 

81 

39.0 

244 

366 

456 

i   5x   9 

110 

37.0 

234 

351 

419 

Continued  on 
next  page. 

60    i  " 

5x12 

111 

40.9 

256 

383 

473 

5x   9 

149 

38.9 

245 

367 

435 

8                     Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines. 

LONG     STROKE     ENGINES 

SHORT     STROKE     ENGINES 

STEAM 

ENGINE 

WATER 

COST  PER  YEAR 

OF  THE  POWEK  NAMED 

ENGINE 

WATER 

COST  PER  YEAR 

OF  THE  POWEU  NAMED 

A 

B                C 

"     :'  E 

l 

o 

H 

I 

I' 

E 

F 

a 

H 

i 

,  „,, 

Size 

t 

and 

TOTAL 

Size 

and 

TOTAL 

NET 

ogja     Point 

Designa 

O, 

Per 

Per  Hour 

For  Coal 

TOTAL, 

Designa 

I 

Per 

Per  Hour 

For  Coal 

TOTAL, 

tion 

f-      o 

I.  B.  P.       for  Net 

tion 

S  2 

I.  U.  P.      for  Net 

HORSE 

of 

«T~ 

0     3 

"-£    c 

per 

Horse 

at  $800 

(Interest 

• 

~«r 

0     S 

«   e 

per        Horse 

at  $8.00 

(Interest 

POWER 

§•§.!  Cut-off 

a"  s 

B 

1 

1 

Hour 

Power 
named 

per  Ton 

Engine 
included) 

£ 

2 

DO 

"o  ^ 

1 

Hour      Power 

named 

per  Ton 

Engine 
included) 

fi  E  o. 

In. 

hi. 

Lbs. 

Lbs. 

la. 

In 

Lbs. 

Lbs. 

5 

60     £  stroke 

6x16      88 

41.5 

259  [     $389 

I 

$489 

6x   9 

104 

40.7 

258 

$386 

$461 

H.  P. 

80    I  stroke 

5x12      71 

45.4 

284        $426 

$511 

5x9      95 

43.7 

264 

$396 

$460 

Concluded. 

60    f   " 

5x12    101 

46.9 

297          445 

530 

5x    9    128 

45.5 

288 

432 

496 

60    £  " 

6x16      50 

51.4       321          482 

577 

6x    9|i    90 

17.7 

•!d2 

453 

524 

10 

100  i  i  stroke 
80    i   " 

6x16    100 
6x16    128 

29.0 
30.2 

362 

377 

$544 
566 

$644 
666 

6x    9    179 
i    6  x    9    231 

26.7 
28.5 

338 
361 

$507 
541 

$582 
616 

HT> 

so 

i  « 

7  x  20      75 

32.4 

400 

600 

710 

7x12    126 

29.1 

364 

546 

629 

.    1   . 

i  " 

8x20      58 

33.0 

408 

612 

745 

8x12 

97 

30.9 

388 

582 

682 

60 

.1  » 

7x20    105 

34.4       425 

637 

747 

7x12    178 

31.7       396 

594 

677 

60 

1      « 

i    8x20 

81 

35.6 

439 

659 

792 

8x12    138 

32.7       409 

613 

713 

60 

*     " 

9x24 

53 

37.4 

460 

690 

850 

;   9x15:     85 

35.0 

432 

648 

768 

100 

i  stroke 

5x12 

129 

33.4      417 

$626 

$716 

5x   9    174 

31.7 

401 

$602 

$670 

100 

1      U 

6x16 

68 

35.8       448 

672 

772 

6x    9    121 

33.2 

420 

630 

705 

80 

1      U 

!   5x12 

162 

34.4       430 

645 

735 

5x    9 

220 

32.9 

416 

625 

693 

80 

1    (( 

6x16      85 

37.2 

465 

698 

798 

6x    9    153 

34.3 

434 

651 

726 

60 

1    it 

6x16    116 

39.4 

492 

739 

839 

6  x   9  !  207 

35.8 

453 

680 

755 

60 

i    u 

7x20 

67 

42.2 

520 

780 

890 

7x12    113 

39.1 

489 

733 

816 

100 

I  stroke 

:   5x12 

113 

39.7 

496 

$744 

$829 

5x   9 

152 

38.2 

484 

$726 

$790 

100    |  " 

6x16      59 

42.2 

528 

792 

887 

6x  9 

106 

39.5 

500 

750 

821 

80    |  " 

i   5  x  12  i  142 

40.9 

511 

767 

852 

;  5x  9 

190 

39.4 

500 

750 

814 

80 

8     " 

6x16      74 

43.7 

546 

819 

914 

j   6x   9 

132 

40.8 

516 

775 

846 

60   I  " 

6  x  16    100 

45.9 

574 

860 

955 

•  ix     !» 

;  179 

42.6 

539 

809 

880 

15 

100 
100 

i  stroke 
ir   " 

7  x  20 
8x20 

87 
66 

29.0 
29.6 

537 

548 

822 

$916 
955 

7x12 
8x12 

145 
112 

27.1 

27.6 

508 
518 

$762 
776 

$845 
876 

H  P 

80    |  " 

7x20 

112:  30.2       559 

839 

949 

7x12 

189 

28.1 

527 

790 

873 

80    i  " 

i    8x20 

86 

31.0       574 

861 

994 

8x12 

145 

29.0 

544 

816 

916 

80 

i   it 

!   9x24 

56 

32.4       592 

888 

1048 

9x15 

90 

30.6 

567 

851 

971 

<;o    I  " 

7x20 

158 

32,1       594 

891 

1000 

7x12 

266 

29.8 

559 

838 

921 

60    1  " 

I    8x20 

122 

33.1 

Hi:; 

920 

1053 

8x12 

207 

30.6 

574 

861 

961 

60    i  " 

1    9x24 

79 

34.9 

638 

958 

1118 

9x15 

127 

32.6 

603 

905 

1025 

60 

i  " 

10x24 

64 

35.6 

652 

979 

1159 

10x15 

104 

33.3 

616 

924 

1104 

100    i  stroke 

6x  16 

101 

33.7 

631 

$948 

$1048 

6x   9 

181 

31.2 

592 

ssss 

$963 

100 

i  " 

7x20 

58  1  35.7 

660 

990 

1100 

7x12 

98 

33.6 

630 

945 

1028 

80 

*  " 

|    6x16 

127    34.9 

654 

981- 

1081 

6x    9 

229 

32.3 

613 

920 

995 

80 

i   " 

7x2u 

74    37.1 

687 

1031 

1141 

7x12 

!  129 

34.4 

645 

968 

1051 

60 

i    a 

7x20 

i  100    39.3 

728 

1092 

1202 

7x12 

j  169 

36.3 

681 

1021 

1104 

Continued  on 
next  page. 

60 

i    « 

8x20 

77 

40.4 

747 

1121 

1254 

8x12 

129 

37.5 

703 

1055 

1155 

Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines.                      9 

LONG     STROKE    ENGINES 

SHORT     STROKE     ENGINES 

STEAM 

ENGINE 

WATER 

COST  PER  YEAR 

OP  THE   POWER   NAMED 

ENGINE 

WATER 

COST  PER  YEAR 

OF  THE  POWER  NAMED 

A 

B              C 

n 

E 

F 

0 

H 

i 

D                 E 

F                 G 

H                         I 

U-8 

Size  and 

TOTAL 

Size  and 

TOTAL 

NET 

•<  £ 

Pnint 

Designa 

Per 

Per  Hour 

For  Coal 

TOTAL. 

Designa 

Per 

Per  Hour 

For  Coal      TOTAL, 

0  0-0 

tion 

3  S 

I.  H.  P. 

for  Net 

tion 

§     * 

I.  H.  P. 

for  Net 

HORSE      '•'•Ig'      of 

Jg 

per 

Horse 

at  $8.00 

(Interest 

3    a 

per 

Horse 

at  $8.00      ('nterest 

I    ® 

££  § 

1        = 

|I 

Hour  '    Power 

on  cost  of 

,    ttnnr        Power 

on  cost  of 

POWER 

|1  7  Cut  oft 

5    1   1 

3 

named 

per  Ton 

Engine 

e       $ 

E 
£ 

named 

per  Ton        En«'ne 

£  2  £ 

included) 

sas, 

In.    |   In 

Lbs. 

I.h-. 

1".         In. 

Lbs. 

Lbs. 

15 

100 

100 

£  stroke 

£   " 

5x12 
6x16 

170 

88 

37.3 
40.1 

699 

752 

$1049 
1128 

$1130 
1223 

5x    9 
6x    9 

228 
159 

35.9 

38.7 

682 
735 

$1022      $1086 
1102        1173 

ii  P 

80 

1   " 

6x16 

111 

41.3 

774 

1161 

1256 

6x    9 

199 

38.7 

735 

1102        1173 

Concluded. 

80 

i   " 

7x20 

65 

43.4 

803 

1205 

1309 

7x12 

108 

410 

769 

1153        1231 

60 

£  " 

7x20 

86 

45.9 

850 

1275 

1379 

7x12 

146 

42.9 

804 

1206        1284 

60 

a    u 

8x20 

66 

47.2 

873 

1310 

1  i:;s 

8x12 

112 

44.0 

825 

1238         i:;:!l 

20 

100 
100 

i  stroke 
i   " 

7x20 
8x20 

115 

88 

27.6 
28.3 

681 
699 

$1022     $1132 
1048       1181 

7x12 
8x12 

194 

149 

25.8 
26.7 

645 

668 

$968 
1001 

$1051 
1101 

H   P 

80 

*   " 

8x20 

114 

29.7 

733 

1100       1233 

8x12    193 

27.8 

695 

1043 

1143 

80 

i  " 

9x24 

74 

31.1       759 

1138       1298 

9x15    120 

29.2  !     721 

1081 

1201 

80 

i  " 

10x24 

60 

31.6 

771 

1156 

1336 

10  x  15      98 

29.9       748 

1122 

1257 

60 

i  " 

9x24 

105 

33.1 

807 

1211 

1371 

9x15    169 

31.1 

768 

1152 

1272 

60 

i  " 

10x24 

85 

34.0 

829 

1244       1424 

10x15     138 

31.8 

785 

1178 

1313 

60 

1  " 

11x30 

56 

35.8 

863 

1295 

1495 

11x18 

94 

33.4 

815 

1222 

1372 

100 

i  stroke 

7x20 

78 

34.3 

847 

$1270 

$1380 

7x12 

131 

31.8 

795 

$1193 

$1276 

100 

i    ii 

8x20 

60 

36.3 

896 

1344 

1477 

8x12    101 

32.8 

820 

1230 

1330 

80 

*   " 

7x20 

98 

35.6 

880 

1319 

1429 

7x12    166 

33.1 

828 

1241  !       1324 

80 

1    u 

8x20 

75 

36.3 

896 

1344 

1477 

8x12 

128 

33.9 

848 

1271 

1371 

60 

*    " 

7x20 

134 

37.4 

923 

1385 

1495 

7x12 

225 

34.8 

870 

1305 

1388 

60 

*  "  ! 

8x20 

102 

38.5       951 

1426       1559 

8x12 

173 

35.7 

893 

1339 

1439 

60 

i  « 

9x24 

67 

40.4 

985 

1481 

1641 

9x15 

108 

37.1 

916 

1374 

1494 

100 

£  stoke 

6x16 

118 

38.4 

960 

$1440 

$1535 

6x   9 

212 

35.8 

906 

$1359 

$1430 

100 

£  " 

7x20 

68 

40.5 

1000 

1500 

1604 

7x12"  116 

38.2 

955 

1433 

1511 

80 

£  " 

7x20 

86 

41.9  !    1035 

1552 

1656 

7xl2l  145 

39.6 

990 

1485 

1563 

80 

£  " 

8x20 

66 

42.6     1052 

1578 

1733 

8x12 

111    40.4 

1010 

1515 

1611 

60 

£  " 

7  x  20 

115 

44.0 

1086 

1630 

1734 

7x12 

195    41.1 

1028 

1542 

1620 

60 

£  " 

8x20 

88 

45.1 

in:; 

1669 

1797 

8x12    149  1  42.2     1055 

1583 

1679 

25 

100 
100 

i  stroke 

i   " 

8x20 
9x24 

110 

72 

27.3 

28.5 

843 

869 

$1264 
1304 

$1397 
1464 

8x12 
9x15 

186 
116 

25.7       803 
27.0       833 

$1205 
1260 

$1305 
1380 

ii.  P. 

80 

1    u 

9x24 

93 

30.0 

915 

1373 

1533 

9x15 

150 

28.3       873 

1310 

1430 

80 

i  " 

10x24 

75 

30.6 

933 

1399 

1579 

10x15 

122 

1  28.9  I      891 

1336  i       1471 

60 

1      U 

9x24 

131 

32.0 

976        1464 

1624 

9x15 

212 

30.1 

929 

1394  i       1514 

60 

1    .. 

10x24 

106 

32.7 

997  '      1496 

1676 

10x15 

172 

30.8 

951 

1427!       1562 

60 

1    « 

11  x  30 

69 

34.6 

1048 

1572 

1772 

11x18 

117 

32.2 

982 

1473 

1623 

60 

i  " 

12x30 

58 

35.0 

1054 

1581 

1801 

12x18 

96 

32.9 

1027 

1541 

1706 

100 

•i-  stroke 

7  x  20 

97 

33.2 

1025 

$1537 

$1647  l 

7x12 

164 

1  30.5 

953 

$1430 

$1513 

100 

i    « 

1   8x20 

75 

33.7 

1041 

1560 

1693 

8x12 

126 

31.6 

988 

1481 

1581 

Continued  on 
next  page. 

80 

i    « 

8  x  20 

94 

35.1 

1083 

1625 

1758 

8x12 

160 

32.8 

1025 

1538 

1638 

1O                  Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines. 

LONG     STROKE     ENGINES 

SHORT     STROKE     ENGINES 

STEAM       1 

ENGINE 

WATER 

COST  PER  YEAR 

ENGINE 

WATER                   COST  PER  YEAR 

1 

OF  THB   TOWER   NAMED 

A 

B 

c 

D 

K 

F 

o 

H                      I 

D 

K 

F                      O                             II                              I 

.  _ 

Size 

and 

TOTAL 

Size  and 

TOTAL 

NET 

<  a 

Pnint 

Designa 

S            Per 

Per  Hour  '   For  Coal 

TOTAL, 

Designa 

I 

Per    iTer  Hour  '  For  Coal 

TOTAL, 

0  °-B 

tion 

3  s    !  '•  H.  P. 

for  Net 

tion 

a  S 

1.  11.  P.      for  Net 

HORSE 

"is 

of 

|  g        per 

Horse        at  $8.00 



o     3 

a  § 

per         Home       at  $8  00 

(Interest 

POWER 

iff  Cut-off 

1 
5 

! 

-9        II 

Hour 

«        'i 

Power 

„                       1.  II:'  llh 

named        per  Ton       .     .    .    .. 

d          M 

J        £ 

f 

Hour       Power 
named 

per  Ton 

on  cost  of 
Engine 

£  g  S 

£ 

C  B  a 

In. 

In. 

1 
Lbs.           Lbs. 

In.       In. 

Lbs.           Lbu. 

25 

80   i 
60    I 

•  stroke 

9x24 
9x24 

1 

61 

83 

36.6 
39.2 

1116 
1195 

$1674 
1793 

$1834 
1953 

9x15 
9x15 

99 
135 

34.6 

36.6 

1068 
1130 

$1602 

1694 

$1722 
1814 

H.  P. 

60    , 

r    " 

10  x  24 

67  ;  39.8 

1213        1820 

2000' 

10x15 

109 

37.4 

1154 

1731 

1866 

Concluded. 

i 

100.  f,troke 

7x20 

85 

39.4 

1216      $1824     $1928 

7x12 

145 

371 

1159 

$1739 

$1817 

100    \ 

L      *' 

8x^0 

65 

39.9 

1231        1847       1975 

8x12 

111 

37.9 

1184 

1777 

1873 

80    { 

I      " 

7  x  20    107 

40.6 

1253i      1880       1984 

7x12 

183 

38.5 

1203 

1805 

1883 

80    1 

L      " 

8x20 

82 

41.4 

1278        1917       2045 

8x12 

138 

39.3 

1228 

1M2 

1938 

80  •  |  " 

!    9x24 

53 

42.9 

1308        1962       2117 

9x15 

87 

40.9 

1262 

1893 

2009 

60    |  " 

8x20 

110 

43.7 

1349        2023 

2151 

8x12 

176 

41.3 

1291 

1936 

2032 

60    i 

t    " 

9  x  24      72 

45.4 

I;;M       2076 

L'-J:  H 

9x15 

116 

43.2 

1333 

2000 

2116 

, 

30 

100 
100 

i  stroke 
1    u 

9  x  24 
10x24 

86 
70 

27.9 

28.2 

1021 
1032 

si  531 
1548 

$1691 

1728 

9  x  15    140  !  26.3 
10x15  ,  113  ;  26.8 

974 
993 

si  |.;i 
1489 

$1581 
1624 

80 

J 

10x24      90    29.8 

1090 

1635 

1815 

10xl5:  146    28.1 

1041 

1561 

1696 

.  P. 

80 

i    " 

11x301!    59 

31.1 

1159        1739 

1939 

11x18      99 

29.3 

1065 

1597 

1747 

60 

i    " 

11  x  30      83 

33.7 

1217 

1825 

2025 

11x18 

140 

31.3 

1145 

1718 

1768 

60 

i    " 

12x30 

70 

34.0 

1229 

1843 

2063 

12x18 

115 

31.9 

1167 

1751 

1916 

60 

i    " 

13x36      49    35.3 

1261        1891 

2144 

13x21      85 

33.0 

1193 

1789 

1979 

100 

%  stroke 

7x20    117    32.2 

1193      $1789 

$1899 

7xl2:!  197 

29:4 

1103 

$1654 

$1737 

100 

^ 

8x20i     89    32.8 

1215        1822 

1955 

8x12    151 

30.5 

1144 

1716        1816 

100 

i 

u 

9x24      58    34.1 

1246        1869 

2029 

9  x  15      94 

32.5 

1204 

1806        1926 

80 

i 

^    tt 

8x20    113    34.2 

1266        1900       2033 

8x12    192 

32.1 

1204 

1806 

1906 

80 

*   " 

9x24      74    35.7 

1306         1959        2119 

9x15    119 

33.8 

1252        1878        1998 

80 

\ 

.   u 

10x24:;    60    36.2 

1324        1986 

2166 

10x15      97 

35.4 

1311 

1967 

2102 

60 

• 

.    « 

9  x  24  ;:  100    37.9 

1387  :       2080 

2240 

9x15    162 

35.6 

1319 

1978 

2098 

60 

\ 

10  x  24      81     38.8 

1420:       2129 

2309 

10  x  15  '  131 

36.4     i;M^ 

2022        2157 

100 

1  stroke 

7x20  :  102    38.4 

1422      $2133     $2237 

7x12    173 

35.9 

1346 

$2019      $2097 

100 

\ 

ifc 

Sxi-'o       7s 

39.2 

1452 

2178 

2306 

8x12 

132 

37.0 

1388 

2081        2177 

80 

\ 

.    " 

8x20      98 

40.6 

1504 

2256 

2384 

8x12  ,  166 

38.5 

1444 

2166        2262 

80 

1   " 

9x24      63    42.0 

15371 

2305 

2460 

9x15;  104 

40.0 

1481 

2222        2338 

60 

f   " 

9  x  24      86 

44.4 

1624|!      2436       2591 

9  x  15    139 

4?,  0 

1556 

2333        2449 

60 

.    " 

10x24 

70  1 

45.0 

1646        2469 

2642 

10xl5|  114 

42.9 

1589 

2383 

2513 

40 

100     i  stroke 

ion    i  « 

10  x  24 
11x30 

93 
61 

27.2 
28.4 

1327! 
1369 

$1990 
2053 

$2170 
2253 

10  x  15     151 
11x18    103 

25.7 
26.7 

1269 
1302 

$1904 
1954 

$2039 
2104 

H.  P. 

80 

i  " 

11x30 

79 

29.9 

1441 

2161 

2361 

11x18    133 

28.1 

1371 

2057 

2207 

80 

i  " 

12x30 

66 

30.3 

1460 

2190 

2410: 

12x18 

111 

28.6 

1395 

2093 

2258 

60 

c  " 

11x30 

111 

32.2 

1552 

2328 

2528 

11x18    187 

29.9 

1459 

2189 

2339 

60 

4 

1C 

12  x  30 

93! 

32.6 

1571 

2357 

2577  ! 

12x18    153 

30.6 

1493 

2240 

2405 

60 

u 

13  x  36 

65 

33.8 

1610 

2414 

2667 

13x21    114 

31.7     1528 

2292 

2482 

Continued  on 
next  p»ge. 

60 

u 

14x36 

56  j   34.2 

1619 

2428 

2704: 

14x21!     98    32.2!    1552 

2328 

2535 

11 

! 

II         II 

Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines.                  11 

LONG     STROKE     ENGINES 

SHORT     STROKE     ENGINES 

STEAM 

ENGINE 

WATER 

COST  PER  YEAR 

ENGINE 

WATFU 

COST  PER  YEAR 

OF  THE   POWER   NAMED 

A                    1       B 

0 

D 

E 

F        |          0 

H                        I 

D 

E 

F                Q 

H 

I 

-•3 

Size 

and 

TOTAL 

Size 

and 

TOTAL 

NET             l$a 

Point 

Designa- 

1 

Per 

I'er  Hour 

For  Coal 

TOTAL,    ; 

Uesigna- 

S. 

Per 

Per  Hour 

For  Coal 

TOTAL, 

o  a  a 

S  s 

.  H.  P. 

for  Net 

ti 

jn 

3  £ 

i.  n.  P.    f0r  net 

HORSE 

of 

0     D 

'•3  S 

per         Horse 

(Interest 

0      3 

*•£    c 

per        Horee 

at  $8.00 

(Interest 

« 

6  £  3 
POWER 

a  g  « 

Cut-off 

5 

| 

a 

1  s 

K 

Hour 

Power 

named 

• 

per  Ton 

Engine 
included) 

S 

Q 

| 

Vj 

I3 

t> 

M 

Hour 

Power 
named 

per  Ton 

Engine 

i   In. 

!u 

Lbs. 

Lbs. 

In. 

In. 

MM. 

Lbs. 

40 

60 

i  stroke  , 

15x36 

49 

34.7 

1652 

$2478 

$2803 

15x24 

74 

33.1 

1595 

$2393 

$2637 

H.  P.       ;100 

2"  stroke 

8x20 

119 

31.5 

1556 

$2333  :    $2466 

8x12 

201 

29.2 

1460 

$2190 

$2290 

Concluded.           100 

\    " 

9x24 

78 

33.0 

1610 

2415  i      2575 

9x15 

126 

30.9 

1526 

2289 

2409 

100 

i  " 

10x24 

63 

33.4 

1622 

2433       2613 

10x15 

102 

31.6 

1560 

2341 

2476 

80 

t  " 

9x24 

98 

34.3 

1673 

2510 

2670 

;    9x15 

159 

32.3 

1595 

2393 

2513 

80 

i  "   ; 

10x24 

79 

34.9 

1702 

2554 

2734 

10x15 

129 

33.0 

1630 

2444 

2579 

60 

i  " 

11x30 

70 

39.0 

1880 

2819       3019 

11x18 

119 

36.2 

1766 

2649 

2799 

60 

i  " 

12x30 

59 

39.4 

1899 

2848  i      3068 

12x18 

100 

37.0 

1817 

2726 

2891 

100 

1  itroke 

8x20 

104 

37.6 

1857 

$2786 

$2914 

1    8x12 

176 

35.6 

1780 

$2670 

$2766 

100 

4  " 

J   9x24 

68 

39.1 

1907 

2861 

3016 

.9x15 

110 

37.2 

1837 

2756 

2871 

80 

*  " 

!    9x24 

85 

40.6 

1980 

2971  1      3126 

i   9x15 

138 

38.8 

1916 

2874 

2990 

80 

i  " 

'  10  X  24 

69 

41.1 

2005 

3007;      3180 

10x15 

112 

39.4 

1970 

2956 

3086 

60 

1  " 

10  x  24 

93 

43.5 

2122 

3183       3356 

10x15 

151 

41.2 

2034 

3051 

3181 

60 

1  "  1 

11x30 

61 

45.4 

2188 

3282 

3475 

11x18 

1(12 

42.8 

2088 

3132 

3277 

50 

100 
100 

•4  stroke  ! 

i  " 

11  x  30 
12x30 

76 
64 

27.6 
27.9 

1663 
1681 

$2494 
2521 

$2694 
2741  i 

11  x  18 
12x18 

128 
108 

25.9 
26.3 

1580 
1604 

$2370 
2405 

$2520 
2570 

H.  P. 

80 

1   «    : 

i  11x30      98 

29.0 

1747 

2620 

2820 

11x18    166 

27.3 

1665 

2498 

2648 

80 

1   " 

12  x  30      83 

29.4 

1771 

2657 

2877 

12x18    139 

27.7 

1689 

2534 

2698 

80 

i  " 

j  13x36      58 

30.2 

1798 

2696 

2949 

!  13x21    100 

28.6 

1723 

2584 

2774 

80 

i  " 

1  14  x  36 

50 

30.6     1821 

2732 

3008 

14  x  21      86 

29.1 

1735 

2603 

2810 

60 

t  " 

H2x30 

116 

31.6     1904 

2856 

3076 

12x18    191 

29.7 

1811 

2717 

2882 

60 

i  " 

13  x  36 

82 

32.8 

1952 

2929 

3182 

13  x  21     142 

30.7 

1850 

2775 

2965 

60 

i  " 

i  14x36 

70 

33.1 

1970  ;      2955 

3231 

:  14x21    122 

31.1 

1873 

2810 

3017 

60 

i  "  j 

15  x  36      61 

33.7  !    2006  '      3009       3334 

1  15  x  24      93 

32.0 

1928 

2892 

3136 

60 

i  " 

16x42      46:  34.5     2029        3044 

3389 

16  x  24      80  ;  32.5 

1958 

2917 

3177 

60 

i  " 

17  x  42      41 

35.0 

2059 

3089 

3464 

17  x  30      57  .  33.6 

2000 

3000 

3276 

100 

^  stroke 

9  x  24      97 

31.7 

1933 

$2899 

$3059 

9x15    157 

29.8 

1840 

$2759 

$2879 

100 

*   "    i 

10x24      79    32.3 

1970,      2954 

3134, 

10x15    127    30.5 

1883 

2724 

2859 

80 

i   " 

10x24      99    33.9 

2067 

3101 

3281 

10x15    161:31.8 

1963 

2944 

3079 

80 

*   " 

11x30      65:35.2 

2120 

3181 

3381 

11x18    109.;  33.2 

2024 

3037 

3187 

80 

i   "    j 

12x30      54    35.8     2157; 

3236 

3456 

12x18      92  i!  33.9 

2067 

3101 

3266 

60 

i   "    i 

11  x  30      88 

37.8 

2227 

3416 

3616 

11x18    149    35.1 

2140 

3210 

3360 

60 

i   "    i 

12x30      74    38.3 

2314 

3472 

3692 

12x18    125  :  35.7 

2177 

3265 

3430 

60 

i   "    I 

13x36i     52  '39.5 

2351 

3527 

3780 

13x21      90 

37.2 

2241 

3361 

3551 

100 

i  stroke  ! 

9x24      85  ;  38.1 

2323  ; 

$3485 

$3640 

9x15    138 

:  36.1 

2228 

$3343 

$3459 

Continued  on 
next  page. 

100 

4   " 

10x24      69    38.6     2354 

3530 

3703 

10x15    111 

36.9 

1 

2278 

3417 

3547 

12                  Tables  showing  Power,  &c,,  of  Non-Condensing  Stationary  Steam  Engines, 

STEAM 

LONG    STROKE     ENGINES 

SHORT     STROKE     ENGINES 

FVrlVK*                        WATFR                    COST  PER  YEAR 

OF  THE   TOWER  NAMED 

ENGINE 

WATER 

COST  PER  YEAR 
OF  THE  POWER  NAMED 

A 

B 

B      ,          C 

D 

E                 F 

G                         H                           I 

D 

E 

F                O                     H                        I 

-•a 

Size 

and 

TOTAL 

Size 

and 

TOTAL 

NET 

<  c 
»I-S     Point 

Designa- 

Per 

""*         i  ii  it 

Per  Hour     For  Coal 

TOTAL, 

Designa- 

I 

Pe'  'I  Per  Hour     For  Coal       T°TAL' 

K  Big 

ti 

Ml 

S  s     I.  H.  P. 

for  Net 

ti 

JU 

a  S 

1.  11.  P. 

for  Net 

HORSE 

of 

o     3 

per 

Horse        at  $8.00      (Inte" 

o   a 
•s   B 

per 

Horse        at  $8.00 

(Interest 

o 

« 

£  R   fl 

~ 

iM 

C 

Hour 

Power 

i 

i 

1  * 

Hour 

Power 

on  cost  of 

POWER         If  3"  Cut-off 

£  2  a> 

'=. 

5; 

E 

IS 

named        per  Ton       inc°^"dj 

- 
— 

E 

GO 

1 

named    |    per  Ton 

Engine 

included} 

h  B  Si 

In. 

In. 

j    Lbs 

Lbs. 

In. 

In. 

Lbs. 

Lbs.       | 

50 

80 
80 

j 

'  stroke 
t   " 

10  x  24 
11x30 

86  !  40.2 
56    41.6 

2451      $3677 
2506        3759 

$3850 
3952 

10x15 
11x18 

140 

95 

38.3 
39.6 

2364     $3546 
2415        3622 

$3676 
3767 

H.  P. 

60 

I 

:      " 

11x30 

76    44.2 

2663        3994       4187 

11x18 

128 

41.4 

2524 

3787 

3932 

Concluded. 

60 

*  " 

12x30 

64    44.5 

2681        4021 

4233 

12x18 

108 

42.2 

2573 

3859 

4018 

60 

\  " 

13  x  36 

45     45.8 

2727  i      4091 

4336 

13x21 

78 

43.6 

_>!;•_'»; 

3939 

4123 

60 

100 
100 

i  stroke 

i  " 

11x30 
12x30 

91 

77 

26.9 

27.2 

1945 

I'.Mifi 

$2917     $3117 
2949       3169 

11x18 
12x18 

154    25.4 

129    25.7 

1550  : 

1880 

$2324 

2821 

$2474 
2986 

H.  P. 

100 

i   " 

13  x  36 

54 

2s.ii 

2000 

3000 

3253 

13x21 

93    26.6 

1923 

2885 

3075 

80 

r  " 

12x30 

99 

28.7 

2075 

3112 

3332 

12x18 

167 

27.0 

1976 

2964 

3129 

80 

u 

13  x  36 

69    29.6 

2114 

3171 

3424 

13x21 

121    27.9     2017 

3025 

3215 

80 

i 

-  « 

14x36 

60  !  29.9 

2136 

3204 

3480 

14  x  21 

H)4    2S.1     2031 

3047 

3254 

80 

i   " 

15x36 

52    30.2 

2157, 

3236 

3561 

15x24 

79 

29.0     2096 

3144 

33S8 

60 

i   " 

14x36 

84 

32.3 

2307 

3461 

3737 

14x21 

146    30.3 

2190 

3285 

3492 

60 

i  " 

15x36 

74    i',-2.7 

2336 

:;;,!  it 

3829 

15x24 

112 

31.1 

2248 

3372 

3616 

60 

i  " 

16x42 

55  !j  33.7 

2379 

3568 

3913 

16x24 

97 

31.7 

2264 

3396 

3656 

60 

17x42 

49    33.9 

2392 

3588 

3963 

17x30 

68 

32.8 

2315 

3473 

3749 

100 

, 

•  stroke 

10  x  24 

94'i  31.6 

2312 

$3468 

$3648 

10x15 

153 

29.7 

2200 

$3300 

$3435 

100 

1 

' 

11  x  30 

62 

33.0 

L^istl 

3578 

3778 

11x18 

104 

30.9 

2261 

3391 

3541 

80 

\ 

11x30 

78 

34.5 

2494 

3741 

3941 

11x18 

131 

32.5 

2378 

3567 

3717 

80 

\ 

.   « 

12  x  30 

65 

34.8 

2516 

3773 

3993 

12x18 

111 

33.0 

2415 

3622 

3787 

60 

\ 

.   " 

12  x  30 

89 

37.2 

2689 

4034 

4254 

12x18 

150 

34.8 

2546 

3820 

3985 

60 

i 

u 

13x36 

62 

38.6 

2757 

4136 

4389 

13x21 

I  OS 

36.2 

2617       3925 

4115 

60 

i 

« 

14x36 

55 

38.8 

2795 

4193 

4469 

14x21 

93 

36.8 

2662 

3993 

4200 

100 

i  stroke 

9x24 

102 

37.1 

2715 

$4072 

$4227 

9x15 

165 

35.3 

2615 

$3922 

$4038 

100 

1 

L    « 

10x24 

83 

37.8 

2766 

4149 

4322 

10x15 

134 

35.8 

2652 

3978 

4108 

100 

i   " 

11  x  30 

54 

39.1 

2827 

4241 

4434 

11x18 

91 

37.2 

2722 

4083 

4228 

80 

i 

1    " 

10  x  24 

104 

39.3 

2876 

4313 

4486 

10x15 

168 

37.6 

2785 

4178 

4308 

80 

i   " 

11x30 

68 

40.7 

2942 

4413 

4606 

11x18 

114 

38.9 

2S.}i; 

4270 

4415 

80 

i   " 

12x30 

57, 

41.1 

2971 

4457 

4669 

12x18 

96 

39.4 

L'^:; 

4324 

4483 

60 

1   " 

11x30 

91 

43.2 

3123 

4684 

4877 

11x18 

154 

40.6 

2971 

4457 

4602 

60 

1 

I    " 

12x30 

77 

43.5 

3145 

4717 

4929 

12x18 

129 

41.2 

3015        4522 

4681 

t;n 

i  " 

13  x  36 

54 

44.8     3200 

4800 

5045 

13x21 

93    42.7 

3087!      4631 

4815 

70 

100 
100 

; 
• 
; 

:  stroke 

t   " 

12x30 
13x36 

89,  26.7 
63  !  27.5 

2252  i    $3378 
2292  !      3437 

$3598 
3690 

12x18 
13x21 

150 
109 

25.3 

2ii.O 

2160 
2193 

$3240 
3290 

$3405 

3480 

H.  P. 

100 

i  " 

14x36 

54 

27.7 

2308        3462 

3738 

14x21 

94 

26.3 

2218 

3327 

3534 

80 

i  " 

13  x  36 

s  1     29.0 

2417        3625 

3878 

13  x  21 

141    27.4 

2311  |      3466 

3656 

80 

i  " 

14x36 

7o 

29.3 

2442 

3662 

3938 

14x21 

121 

27.7 

2336 

3504 

3711 

80 

i  " 

15x36 

61:  29.6 

2467 

3700 

4025 

15x24 

92 

28.5 

2404 

3606 

3850 

Continued  on 
next  page. 

80 

i  " 

16x42 

45    30.4 

2504 

3755 

4100 

16x24 

80 

28.8 

2400        3600 

3860 

Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines.                  13 

LONG     STROKE     ENGINES 

SHORT     STROKE    ENGINES 

STEAM 

ENGINE 

WATER 

COST  PER  YEAR 

ENGINE                      WATER                   COST  PER  YEAR 

OP  THK    POWKR  NAMED 

OF  TUB  POWER  NAMED 

A                          B               C 

U                 E 

F 

0 

H                        I 

D 

£ 

F 

G 

H                         I 

-*i<  ,5 

Size 

and 

TOTAL 

Size 

and 

TOTAL 

NET            »  f  .a 

Point 

Designa-     £ 

Per 

Per  Hour 

For  Coal 

TOTAL, 

Designa 

I 

Per 

Per  Hour      For  Coal 

TOTAL, 

0  -C 

tion          «  «      |.  H.  V. 

for  Net    , 

tion 

BQ      ft) 

C    £ 

I.  0.  P. 

for  Net 

HORSE        r»|e        of 

I  | 

per 

Horse      :  at  S8.00 

(Interest 

1  3 

per 

Horse    ''  at  $8.00 

(Interest 

q 

£  £3 

a 

1        -3B 

Hour 

Power 

on  cost  of 

i 

1 

1* 

„ 

Power 

on  cost  of 

POWER         Jf  I*  Cut-off 

5 

Be 

w     '  t£ 

named         per  Ton 

Engine 

5 

02 

I 
s 

Hour 

named 

per  Ton 

Engine 

£  S  £ 

i     CM 

included) 

v\ 

included) 

a-  a  o, 

In. 

In. 

Lbs. 

Lbs. 

In. 

in. 

Lbs. 

I.I.S. 

70  -8 

i  stroke 
i   " 

15x36 
16x42 

86    32.1 
64  1  33.0 

2675 
2717 

$4013 

4076 

$4338 
4421 

'  15  x  24 
16x24 

130 
114 

30.5 
31.0 

2572 
2583 

$3858 
3875 

$4102 
4135 

60 

i  " 

17x42      57 

33.2 

2734 

4101 

4476 

17x30 

79 

32.2 

2683 

4025 

4301 

H.  P.          60 

i  " 

19x48 

t)O 

34.8 

2832 

4248 

4674 

19  x  30 

64 

32.7 

2706 

4059 

4379 

Concluded. 

100 

4  stroke 

11  x  30 

72 

32.1 

2707;    $4061 

$4261 

11x18 

121 

30.3 

2587 

$3880 

$4030 

100 

4  "  ; 

12x30 

60 

32.7 

2758        4137 

4357 

12x18 

102 

30.7 

2621 

3931 

4096 

80 

4  "  ! 

11x30 

91 

33.8 

2851        4276 

4476 

11x18    153 

31.8 

2714 

4071 

4221 

su    |  « 

12x30 

76 

34.3 

2893 

4339 

4559 

12xl8p  129 

32.4 

2766 

4149 

4314 

80 

4  " 

13  x  36      53 

35.1 

2925 

4388 

4641 

13  x  21      93    33.3 

2808 

4213 

4403 

60 

4  " 

13  x  36      73 

37.7 

3142 

4712 

4965 

13  x  21    126    35.2 

2970 

4455 

4645 

60 

4  " 

14x36 

63 

38.0 

3167 

4750 

5026 

14x21    108 

36.0 

3036 

4554 

4761 

60 

4  " 

15x36 

55 

38.6 

3217 

4825 

5150' 

15  x  24 

83 

37.0 

3120 

4680 

4924 

60 

4  " 

16x42 

40 

39.7 

3269 

4904 

5249 

,16  x  24 

72 

37.4 

3140 

4710 

4970 

LOO 

1  stroke 

10  x  24      96    37.1 

3167      $4750 

$4923 

10x15 

156 

35.3 

3051 

$4576 

$4706 

100 

1   " 

11x30      63    38.4 

3239 

4858 

5051 

11x18 

106 

36.5 

3116 

4674 

4819 

80 

1   " 

11x30      79    40.1 

3382 

5073 

5266 

.11x18 

133 

38.3 

3270 

4904 

5049 

80 

1   " 

12  x  30 

66    40.5 

3416 

5123 

5335 

12x18 

112 

38.8 

3312 

4968 

5127 

80 

i  " 

13x36 

46 

41.4 

3450        5175 

5420 

13x21 

81 

39.7 

3342 

5013 

5197 

60 

£•" 

12x30 

89 

42.8 

3610        5414 

5626  i 

12x18    150 

40.4 

3449 

5173 

5332 

60 

i  " 

13x36 

63 

44.0 

3667 

5500 

5745 

13x21 

109 

41.7 

3517 

5276 

5460 

60    |  " 

14x36 

54 

44.4 

37ii() 

5550 

5817 

14  x  21      93 

•1-_M 

3576 

5364 

5564 

80   S 

4  stroke 
i   " 

13  x  36      72 
14  x  36  i    62 

27.0 
27.2 

2571'    $3857 
2590        3886 

$4110 
4162 

!  13x21 
14x21 

124 
107 

25.7 

25.8 

2477 
2488 

$3716 
3732 

$3906 
3939 

H.  P.  io° 

i   " 

15x36      54    27.5 

2619        3929 

4254 

15x24 

82 

26.5 

2554 

3831 

4075 

80 

i   " 

14x36:     80  ::  28.8 

2743        4114 

4390 

14x21 

138 

27.2 

2622 

3933 

4140 

80 

i   " 

15  x  36      70 

29.1 

2771        4157 

4482 

15x24    106 

27.9 

2689 

4034 

4278 

80 

i  " 

16  x  42      52 

29.8 

2805        4207 

45521 

i  16x24 

92 

28.4 

2705        4058 

4318 

80 

i  " 

17x42      46 

30.0 

2824 

4235  1      4610 

17  x  30 

64 

29.0 

2762        4143 

4419 

60 

i  " 

16  x  42      73 

32.5 

3058 

4588  1      4933 

16  x  24 

130 

30.3 

2886  ;,     4329 

4589 

60 

i  " 

17x42      65  i  32.6 

3068        4602 

4977 

i  17x30 

90 

31.6 

3009        4519 

4795 

60 

i  " 

19x48      45    33.8 

3181 

4772 

5198 

19  x  30 

73 

32.2 

3030 

4545 

4865 

100 

4  stroke 

11  x  30      82 

31.7 

3055 

$4583 

$4783 

11x18 

138 

29.7 

2898 

$4346 

$4496 

100 

4   " 

12  x  30      69 

32.1 

3094        4641 

4861 

:  12X18 

116 

30.2 

2946        4420 

4584 

100 

4   " 

13  x  36      48 

33.1 

3152:      4728 

4981 

13x21 

84 

31.3 

3017  ,      4525 

4715 

80 

4   " 

12x30      87    33.7 

3248  :      4872 

5092 

'l2x!8!  148 

31.7 

3093        4639 

4804 

80 

4  " 

13x36:     61 

34.6 

3295 

4943 

5196 

1  13x21    106 

32.7 

3152 

4728 

4918 

80 

4  " 

14x36      53 

34.9 

3324 

4986 

5262 

14x21 

91 

33.1 

3190 

4785 

4992 

60 

4  " 

13x36      83 

37.2 

3543 

5314 

5567 

13x21 

144 

34.7 

3344 

5016 

5206 

60 

4  " 

14x36      71 

37.5 

3571 

5357 

5633 

14x21 

124 

35.2 

3393        5090 

5297 

Continued  on            />A 
next  page. 

4  " 

15x36      62 

38.0 

3619 

5429 

5754 

15x24 

95 

36.2 

3489        5234 

5478 

14                  Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines.  ' 

Hi 

LONG     STROKE     ENGINES 

SHORT     STROKE     ENGINES 

STEAM 

ENGINE 

WATER 

COST  PER  YEAR 
OP  THE  POWER   NAMKII 

ENGINE 

WATER 

COST  PER  YEAR 
OP  THK  POWER  NAMED 

A 

u 

c 

D                    K 

F 

'. 

M                       I                        D                  B 

F 

o 

H 

I 

j." 

Size 

and 

TOTAL 

[  Size 

and 

TOTAL 

NET 

s  §•? 

Point 

Designa-      |_ 

Per 

Per  Hour 

For  Coal  ,    TOTAL,       Designa-      | 

Per 

Per  Hour 

For  Coal 

TOTAL, 

tion         «  » 

1.  H.  P. 

for  Net 

tion           .  s 

I.  H.  P. 

for  Net 

HORSE 

•«  s 

of 

c    a 
S    c 

per 

Horse 

at  $8.00      <Intere8t 

0     3 

-j   c 

per 

Horse 

at  $8.00 

(Interest 

£  s  i 

d 

S           S   3 
O 

n 

Power 

on  cost  of  i 

B 

•i    1  ^ 

Tr 

Power 

on  cost  of 

POWER 

if" 

Cut-off 

5 

1    .   | 

named 

per  Ton 

Engine 

5 

1     s 

Hour 

named 

per  Ton 

Engine 

,  £  S  5 

included) 

included) 

£  a  & 

In. 

In. 

Lbs. 

Lbs. 

In. 

ID.    i 

u.,. 

Lbs. 

80 

80 

60 

£  stroke 
i    " 

16  xi^      46 
17  x  42      41 

39.0 
39.2 

3671 

3689 

$5506 
5534 

$5851 
5909 

!  16  x  24      82 
17  x  30      65 

36.8 
37.4 

3505 

3657 

flpO^O  i 

5485 

$5517 
5761 

H.  P.        1ft0 

Concluded. 

f  stroke 

11x30      72 

37.8 

3643 

$5465     $5658  ^ 

i  11x18    121 

35.9 

3502 

$5254 

$5399 

100 

1   " 

12x30      60 

|  38.3 

3692 

5537       5749 

12x18    102 

36.3 

3541 

5312 

5471 

80 

1" 

12  x  30      76 

40.0 

3855 

5788  ;      5995  : 

12xl8;  128 

37.9 

3698 

5546 

5705 

80 

*•« 

13x36      53 

40.8 

3885 

5829       6074 

13x21      92 

39.2 

3774 

5660 

5844 

60 

*" 

:  13  x  36      72 

43.3 

4124 

6186 

6431: 

13x21    124 

41.1 

3962 

5943 

6127 

60 

1   " 

:  14x36      62 

43.7 

4162 

6243       6510 

14x21    107 

41.6 

4009 

6019 

6219 

60 

8     it 

,  15  x  36      54 

1-4.2 

4210 

6314       6630  ;|  !5x24 

82 

42.6 

4106 

6159 

6396 

II 

90 

100    }  stroke 
100    i   " 

!  13x36 
14x36 

81 
69 

26.7 
26.8 

2861 
2871 

$4291 
4307 

$4544    13x21 
4583    14x21 

140 

120 

25.3 

25.5 

2743 

2765 

$4115 
4147 

$4305 
4354 

VX     V/ 

100   i  " 

15x36 

61 

27.1 

2904 

4355 

4680 

15x24 

92 

26.2 

2841 

4262 

4506 

H.  P. 

100  |  "  ; 

i  16x42 

45 

27.7 

2933 

4399 

4744 

16x24 

80 

26.4 

2829 

4244 

4504 

80 

i  ||    , 

15x36 

78 

28.8 

3086 

4629 

4954 

15x24 

119 

27.6 

2993 

4489 

4733 

80 

16x42 

58 

29.4 

3113 

4670 

5015 

16  x  24 

103 

27.9 

2989 

4484 

4744 

80 

i  " 

17x42 

52 

i  29.6 

3134 

4701 

5076 

;  17  x  30 

71 

28.9 

3097 

4645 

4921 

60 

i  " 

16x42 

82 

31.9 

3378 

5067 

5412 

16x24 

145 

30.0 

3214 

4821 

5081 

60 

••  " 

17x42 

73 

32.2 

3409 

5114 

5489 

17  x  30 

101 

31.1 

3334 

5001 

5277 

60 

..  « 

19x48 

50 

33.4 

:;  I'.i.'i 

5243 

5669 

!  19x30 

82 

31.7 

3354 

5031 

5351 

60 

'.  .  " 

21x48 

44 

33.4 

-I:*:,        5243 

5731; 

21x30 

67 

32.3 

3420 

5130 

5496 

100 

£  stroke 

:  11x30 

92 

31.3 

3394     $5091 

$5291 

1  11x18 

155 

29.2 

3205 

$4809 

$4959 

100 

k   " 

;  12  x  30 

78 

31.6 

3427 

5140 

5360 

:  12x18 

131 

29.7 

3260 

4890 

5055 

100 

1  "  : 

13x36 

54 

32.6 

3493 

5239 

5492 

18x21 

94 

30.9 

3351 

5026 

5216 

80 

i   "    ; 

12x30 

98 

33.2 

3600 

5400 

5620 

12x18 

166 

31.3 

3435 

5153 

5318 

80 

\  " 

13  x  36 

69 

34.1 

3654        5480 

5733 

!  13  x  21 

119 

32.4 

3513 

5270 

5460 

80 

i  " 

14  x  36 

59 

34.4 

3686        5529 

5805 

.14x21 

103 

32.7 

3546 

5319 

5526 

80 

k  " 

15  x  36 

52 

34.7 

3718       5577 

5902 

1  15x24      78 

33.7 

3654        5481 

5725 

60 

k  " 

14x36 

80 

36.9 

3954 

5930 

6206 

:  14x21 

139 

34.7 

3763       5644 

5851 

60 

*  !! 

15  x  36 

70    37.3 

3996 

5995 

6320 

1  15x24  ;  106 

35.6 

3860        5790 

6034 

60 

16x42 

52 

38.4 

4066 

6109 

6454 

1  16x24      93 

36.1 

38tW 

:>.su2 

6062 

60 

i  a 

17  x  42 

46  |  38.7 

4098 

6146 

6521 

17x30 

64 

37.5 

4018        6027 

6303 

100 

I  stroke 

1  11x30 

81 

37.3 

4045 

$6067 

$6260 

'11x18 

136 

35.5 

3896:1    $5845 

$5990 

100 

I   "    • 

12x30 

68 

378 

4099 

6148 

6360 

i  12x18 

114 

359 

3940        5910 

6069 

100 

f   " 

13x36 

48 

38.7 

4146 

6219 

6464 

1  13x21 

83 

37.0 

4012|!      6018 

6202 

80 

1   <-' 

i  12x30 

85    39.5 

4283 

6425 

6637 

12x18 

144 

37.7 

4162        6243 

6402 

80 

i   " 

13x36 

60 

40.3 

4318 

6477 

6722 

13x21 

104 

38.6 

4186        6278 

6462 

80 

A   u 

i  14x36 

53 

40.6 

4350 

6525 

6792 

14  x  21 

89 

390 

4280 

6345 

6545 

60 

i  "  : 

13  x  36 

81 

42.9 

4596 

6895 

7140 

13x21 

140 

40.4 

4381 

6572 

6756 

60 

i  " 

:  14  x  36 

69 

43.1 

4618 

6927       7194 

14x21 

120 

41.0 

4446        6669 

6869  i 

60 

1  "  : 

!  15  x  36 

60 

43.7 

4682 

7023  .      7339 

15x24 

92 

42.0 

4554        6831 

7068 

60 

f  " 

16  x  42 

45 

44.7 

4733 

7099 

7434 

16x24 

80 

42.5 

4554        6831 

7082 

Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines.                  15 

STEAM 

LONG     STROKE     ENGINES 

SHORT     STROKE     ENGINES 

ENGINE 

WATER 

COST  PER  YEAH 

OP  THE    POWKR  NAMED 

ENGINE 

WATER 

COST  PER  YEAR 

OP  THE   POWER  NAMED 

A 

B 

c- 

D 

r; 

F 

G 

B 

I 

D 

E 

K 

a 

a 

I 

+* 

Size 

and 

TOTAL 

Size  and 

TOTAL 

NET 

»  °J= 

Point 

Designa- 

I 

Per 

Per  Hour 

For  Coal 

TOTAL, 

Designa 

I 

Per 

Per  Hour 

For  Coal 

TOTAL, 

1  =  1 

tiou 

<n     a> 
o    "3 

I.  H.  P. 

for  Net 

tion 

II 

I.  H.  P. 

for  Net 

HORSE         a'Zs 

of 

V 

'•£      S3 

per 

Horse 

at  $8.00 

(  ii  ere 

. 

=   S 

per 

Horse 

at  $8.00 

(Interest 

£  »  § 
POWER          If" 

Cut-off 

E 
Q 

a 

r 

Hour 

Power 
named 

per    Tun 

on  cost  of 
Engine 

8 

i 

| 

I5 

Hour 

Power 
named 

per  Ton 

on  cost  of 
Engine 

U    ®    0) 

0* 

included) 

a,  B  a 

In. 

In. 

Lbs.     |       Lbs. 

IT 

In. 

Lbs. 

l.bs. 

100 

100 
100 

i  stroke 
i   " 

14x36 
15x36 

77 
67 

26.5 

26.8 

3014 
3190 

$4521 
4786 

$4797 
5111 

14x21 
15  x  24 

134 

102 

25.2 

25.8 

3036 
3109 

$4554 
4663 

$4761 
4907 

100 

1      U 

i  16  x  42 

50 

27.4 

3224        4835 

5180  : 

16  x  24 

88 

26.1 

3107 

4660 

4920 

II.  p. 

100 

i  " 

17x42 

45 

27.5 

3235 

4853 

5228; 

17x30 

61 

26.9 

3203 

4804 

5080 

80    i  « 

15x36 

87 

28.3 

3370 

5055 

5380 

15x24 

132 

27.2 

3277 

4916 

5160 

80    |  " 

16x42 

65 

29.0 

3424 

5135 

5480  :, 

16  x  24 

115 

27.5     3274 

4911 

5171 

80    |  " 

17x42 

57 

29.3 

3488 

5232 

5607 

17x30 

79 

28.5 

3393 

5089 

5365 

80    ^  " 

19x48 

40 

30.1 

3500 

5250 

5676 

!  19  x  30 

64 

28.9 

3400 

5100 

5420 

60    - 

17x42 

81 

31.8 

3741 

5612 

5987 

17x30'  112 

30.7 

3655 

5482 

5758 

60  1  i  " 

19x48 

56 

32.9 

3826 

5738 

6164 

19  x  30      91 

31.2 

3671 

5506 

5826 

60   -t  " 

21x48 

49 

32.9 

3826;       5738 

6226 

21  x  30  1     74 

31.9 

3752 

5628 

5994 

60 

i  " 

23  x  54 

34 

33.9 

3897 

5846 

6396 

,  23  x  36 

51 

32.8 

3814 

5721 

6133 

100     4  stroke 

12x36 

86 

31.3 

3783 

$5659 

$5879 

12x18 

146 

29.2     3561 

$5342 

$5507 

100    |  " 

13x36 

60 

32.1 

3822 

5732 

5985' 

13x21 

105 

30.2     3639 

5458 

5648 

100!  £   " 

14x36 

52 

32.2 

3833        5750 

6026 

14x21 

90 

30.7     3700 

5550 

5757 

80    |  " 

13x36 

76 

33.7 

4012  !J      6017 

6270 

13x21 

132 

32.0  !    3855 

5783 

5973 

80    £  " 

14x36 

66    34.1 

4060 

6080 

6356 

14x21 

114 

32.3     3892 

5838        6045 

80    £  " 

15x36 

56 

34.4 

4095 

6143 

6468 

15x24 

87 

33.1     3988 

5982        6226 

80    |  " 

16x42 

48 

34.6 

4071  :      6107 

6452 

16x24 

75 

33.4     3979 

5968        6228 

60    £  " 

15  x  36 

78 

37.0 

4405        6607       6932 

15x24 

118 

35.1     4229 

6343 

6587 

60  !  |  " 

16x42 

58 

37.8 

4447 

6671 

7016 

16x24 

103 

35.6     4238 

6357 

6617 

60    |  " 

17  x  42      51 

38.2 

4494 

6741 

7116 

17x30 

71 

37.1 

4417 

6625 

6901 

1  Af  1       8 

It  stroke  ' 

11x30      90 

37.0 

44581!   $6687 

$6880 

11x18 

151 

35.0 

4268 

$6402 

$6547 

100    |  " 

12x30      75    37.3 

4494        6741 

6953 

12x18 

127 

35.5     4329 

6494        6653 

100    |  " 

13  x  36 

53 

38.3 

4560 

6839 

7084 

13x21 

92 

36.5     4398 

6596     _  6780 

80  i  |  " 

12x30 

95 

39.0 

4699        7048 

7260 

12x18 

160 

37.3     4549 

6824 

6983 

80  i  1  " 

13x36 

67    39.9 

4750        7125 

7370    13x21 

115 

38.3     4614 

6922 

7106 

80    f  " 

14x36      59    40.1 

4774       7161 

7428 

14  x  21  i    97 

38.7     4663 

6994 

7194 

80    f  " 

15x36      50 

40.6 

4883 

7325 

7641    15  x  24      76 

39.4;   4747 

7120 

7357 

60 

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14x36      77 

42.7 

5083 

7625 

7892    14  x  21  i  134 

40.4     4865 

7297 

7497 

60    |  " 

15  x  36      67 

43.2 

5142 

7714 

8030  1  15x24    102 

41.3     4976 

7464 

7701 

60    *  " 

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50 

44.1 

5188 

7782 

8117 

16  x  24      88. 

42.0     5000 

7500 

7751 

'.    60    1  " 

17x42 

44 

44.4 

5224  i 

7S36 

8201 

17x301 

61 

43.4 

5143 

7715 

7981 

j  125  SB 

i  stroke 
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15x36 
16x42 

84 
63 

26.1 

26.7 

3908 
3926 

$5862 
5890 

$6187 
6235 

1 

15x24    128 
16x24    111 

25.1 
25.4 

3780 

3779 

$5670      $5914 
5668  '•       5928 

HP        :100i" 

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56) 

26.8 

3941 

5912 

6287    17  x  30      77 

26.2 

3900 

5850 

6126 

;       80 

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17x42 

72 

28.4 

4176 

6165 

6540  i  17x30  1|    99 

27.7 

4121 

6182 

6458 

80 

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19x48 

50 

29.4 

4273 

6410 

6836    19  x  30      80 

28.1 

4132 

6198 

6518 

80 

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21x48 

43 

29.4 

4273 

6410 

6898    21x30 

66 

28.6 

4266 

6309 

6675 

60 

i  "   i 

19x48 

60 

31.9 

4637 

6955 

7381    19  x  30 

113 

30.4 

4471 

6706 

7026 

Continued  on 
next  page. 

60 

i  " 

21x48 

61 

32.1 

4666 

6999 

7487    21  x  30 

93 

30.9 

4545 

6818 

7184 

16                   Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines, 

LONG     STROKE    ENGINES 

SHORT     STROKE     ENGINES 

STEAM 

ENGINE 

WATER 

COST  PER  YEAR 

OF  THE   POWER   NAMED 

ENGINE 

WATER 

COST  PER  YEAR 

OT  THE  POWEB  NAMED 

A 

B 

c 

D 

E 

P 

o 

II 

i 

D 

E 

F 

a 

H 

i 

•M  M 

Size 

and 

TOTAL 

'  Size 

and 

TOTAL 

NET 

^  °JA 

Point 

Designa-      e, 

Per 

Per  Hour 

For  Coal 

TOTAL, 

Designa- 

1 

Per 

Per  Hour 

For  Coal 

TOTAL, 

-   —  z 

ti 

S  3 

I.  H.  P. 

for  Net 

ti 

)n 

00       « 

C    •*-> 

I.  H.  P. 

for  Net 

HORSE 

111 

of 

|| 

per 

at  $8.00 

(Interest 
on  cost  of 

•J  g 

3    — 

per 

Horse 

at  $8.00 

(Interest 
on  cost  of 

9 

^ 

01 

a 

o 

Power 

E 

•3  * 

Power 

POWER 

*-  £  aj 

Cut-off 

:  s 

GO 

1 

rlOu." 

named 

per  Ton 

Engine 
included) 

5 

n 

1 

jiour 

named 

per  Ton 

Engine 
included) 

fin    £    ft 

In. 

In.   1 

Lbs. 

Lbs. 

In. 

In 

Lbs. 

Lbs. 

125 

60 
60 

i  stroke 
i   " 

1  23  x  54      42 
24  x  54      39 

33.2 
33.2 

4770 

4770 

$7155 
7155 

$7705 
7770 

23x36 
24x36 

64 
59 

31.9 

32.0 

4637 

4651 

$6955 
6977 

$7367 

7438 

H.  P. 

Concluded. 

i  stroke 

13  x  36      76 

31.3 

4658 

$6987 

$7240 

13x21    131 

29.2 

4398 

$6596      $6786 

100 

1       U 
2 

14x36:     65 

31.4 

4673 

7009 

7285 

14x21    113 

29.7 

4472 

6708 

6915 

100 

Ir   " 

15x36      57 

31.7     4717        7076 

7401 

15x24      86 

305 

4593 

6889 

7133 

100 

T    a 

16x42      43 

32.3 

4739        7109 

7454 

16x24      77 

30.7 

4569 

6853 

7113 

80 

1    u 

14x36 

82 

33.1 

4325        7388 

7664 

14x21    125 

31.8 

4789 

7183 

7390 

80 

i    a 

15x36 

71 

33.6 

5000        7500 

7825 

15x24    109 

32.3 

4864 

7296        7540 

80 

i    u 

16x42 

53 

34.3 

5044 

7566 

7911 

16  x  24      95 

32.6 

4851 

7277 

7537 

80 

1       U 

17x42 

47 

34.4 

5059 

7588 

7963 

17x30 

65 

33.6 

5000 

7500 

7776 

60 

i    a 

16x42 

73 

36.9 

5426 

8140 

8485 

16x24 

128 

34.5 

5169 

7753 

8013 

60 

1      U 

17x42 

64 

37.1 

5456 

8184 

8559 

17  x  30 

89 

36.0 

5357 

8036 

8312 

60 

1      U 

19x48 

45 

38.3 

5567 

8350 

8776 

19x30 

72 

36.5 

5368 

8052 

8372 

100 

I  stroke 

12x30 

94 

36.5 

5497 

$8245 

$8457 

12x18 

159 

34.6 

5274 

$7911 

$8070 

100 

1   " 

13x36 

66 

37.3 

5551 

8326 

8571 

13x21    115 

35.5 

5346 

8020 

8204 

100 

1   " 

14x36 

57 

37.6 

5595 

8393 

8660 

14x21      99 

35.8 

5392 

8088 

8288 

100 

1   " 

15x36 

50 

37.8 

5625 

8438 

8754 

15x24 

75 

36.7 

5525 

8288 

8525 

80 

1   " 

13x36 

84 

39.1 

5819 

8729 

8974 

13x21 

144 

37.5 

5648 

8472 

8656 

80 

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14x36 

73 

39.4 

5863 

8795 

9040 

14x21 

124 

37.7 

5677 

8515 

8715 

80 

8     (( 

15x36 

62 

39.8 

5923 

8884 

9200 

15x24 

95 

38.6 

5813 

8720 

8957 

80 

3     a 

16x42 

47 

40.4 

5941 

8912 

9247 

16x24 

82 

38.9 

5790 

st;s:> 

8936 

80 

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17x42 

41 

40.6 

5971 

8957 

9322 

17x30 

57 

39.8 

5923 

8884 

9150 

60 

8     U 

15x36 

84 

42.1 

6265 

9397 

9713 

15x24 

127 

40.4 

6080 

9120 

9357 

60 

a    u 

16  x  42 

63 

43.1 

6338 

9507 

9842 

16  x  24 

111 

40.8 

6072 

9108 

9359 

60 

1   " 

17  x  42 

55 

43.4     6382 

9574 

9939 

17  x  30 

77 

42.2 

6280 

9420 

!HiS6 

150 

100 
100 

i  stroke 
i   " 

16x42 
17  x  42 

75 
67 

26.2 
26.3 

4624 
4641 

$6935 
6962 

$7280 
7337 

16x24 
17x30 

133 

92 

24.9 
25.7 

4446 
4590 

$6670 

6885 

$6930 
7161 

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100 

i  " 

19x48 

46 

26.9 

4692 

7038 

7464 

19x30 

75 

25.9 

4571 

6856 

7176 

.       1     . 

100 

i  " 

i  21x48 

40 

27.1 

4704 

7055 

7543 

21x30 

61 

26.4 

4659 

6988 

7354 

80 

i  " 

19x48 

60 

28.7 

5006 

7509       7935 

19  x  30 

96 

27.6 

4871 

7306        7626 

80 

i  " 

:  21  x  48 

52 

28.9 

5041 

7561       8049 

21x30 

79 

28.0 

4941 

7413        7779 

80 

i  " 

23  x  54 

36 

29.6 

5103 

7655 

8205 

23  x  36 

54 

28.7 

5006 

7509        7921 

60 

i  " 

21x48 

73 

31.4 

5477 

8216  i      8704 

21x30 

112 

30.2 

5330  ! 

7995  :       8361 

60    i  " 

23  x  54 

50 

32.6 

5621 

S431 

8981 

23x36 

76 

31.3 

5469 

8188        8600 

60 

i    n 

24x54 

46 

32.7 

5638 

8457 

9072 

24  x  36 

70 

31.4 

5477 

8215        8676 

60 

i    " 

26x54 

40 

32.7 

5638 

8457 

9112 

26  x  42 

51 

32.0 

5581 

8372        8863 

60 

i    " 

27x60 

33 

33.1 

5642 

8463       9178 

27x42 

49 

32.2 

5552 

8328        ^t'>4 

60 

i    " 

28  x  60 

30 

33.3 

5619 

8429 

9205 

28x48 

39 

32.6 

5621 

8432        9014 

100 

i  stroke 

14x36 

78 

30.7 

5482 

$8223 

$8499 

14x21 

135 

28.9 

5223 

$7834 

$8041 

Continued  on 
next  page. 

100    |  « 

15x36 

68 

31.0 

5536 

8304 

8629 

15  x  24 

103 

29.8     5409 

8119 

8363 

Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines.                  17 

LONG    STROKE     ENGINES 

SHORT     STROKE     ENGINES 

STEAM 

1 

ENGINE 

WATER 

COST  PER  YEAR 

OF   TUB   POWER    NAMED 

ENGINE 

WATER 

COST  PER  YEAR 

OF  THE  POWER  NAMED 

A 

B 

c 

U 

K 

1 

G 

H 

i 

D 

E 

F 

o 

H 

I 

-•3 

Size 

and 

TOTAL 

Size  and 

TOTAL 

NET 

•^  c 
S  S'S 

Point 

Designa- 

s 

Per 
In   D 

Per  Hour     For  Coal 

TOTAL, 

Designa 

& 

Per 

i  if  i> 

Per  Hour 

For  Coal 

TOTAL, 

£  -c 

ti 

jn 

Q    S 

.  B.  P. 

for  Net 

tion 

e  -2 

1.  U.  r.       for  Net 

HORSE 

*|e 

of 

0     3 

per 

Horse 

at  $8.00 

(Interest 
on  cost  of 

0     3 
'.£     — 

per          Horse 

at  $8.00 

(Interest 

S 

» 

POWER 

II  1 

r*  a  0 

£ 
ci 
5 

I 

O 

Hour 

Power 
named 

per  Ton 

Engine 
included) 

1        | 

0 

H 

Hour 

Power 
named 

per  Ton 

Engine 
included) 

S  S  S, 

In. 

In. 

Lbs. 

Lbs. 

In.       In.    ; 

Lbs. 

Lhs. 

150 

100 
100 

^  stroke 
1    " 

16x42 

17x42 

51 
45 

31.7 
32.0 

5594 
5647 

$8391 
8471 

$8736 
8846 

16  x  24 
17x80 

92 
68 

30.0 
30.7 

5357 

5480 

$8035 
8220 

$8295 
8496 

H.  P. 

15x36 

85 

32.8 

5857 

8786 

9111 

15x24 

131 

31.4  1    5675 

8512 

8756 

Concluded.              °"  i    2 

16  x  42      64 

33.6 

5929 

8894 

9239 

16x24 

114 

32.0  1    5714 

8571 

8831 

80    }  « 

17x42,!    57 

33.8 

5964 

8947 

9323 

17x30 

78 

33.0     5893 

8839 

9115 

80    £  " 

19  x  48      40 

34.6 

6035 

9053 

9479 

19x30 

63 

33.3 

5877 

8815 

9135 

60    i  " 

17x42J    77 

36.1 

6371 

9556 

•9931 

17  x  30 

107 

35.0 

6250 

9370 

9646 

60   £  ". 

19x48      53 

37.5 

6541 

9811 

10237 

19  x  30 

75 

36.3 

6406 

9609 

9929 

60   $  " 

21x48 

46 

37.8 

6594 

9891 

10379 

21x30 

71 

36.3 

6406 

9609 

9975 

100!  |8troke 

13x36 

79 

36.7 

6554 

$9830 

10075 

13x21 

138 

34.9 

6307 

$9461 

$9645 

100    f  " 

14x36 

68 

36.9 

6589 

9884 

10151 

14x21 

118 

35.3 

6379 

9568 

9768 

100    f  " 

15x36 

60 

37.1 

6625 

9938 

10254 

15x24 

91 

35.9 

6488 

9732 

9969 

100    |  " 

16x42 

54 

37.1 

6547 

9821 

10156 

16x24 

78 

36.3 

6482 

9723 

9974 

80    |  " 

14x36 

88 

38.7 

6911 

10367 

10634 

14x21 

149 

370 

6687 

10030 

10230 

80    f  " 

15  x  36      75 

39.0 

6964 

10446 

10762 

15x24 

114 

37.9 

6849 

10273 

10510 

80  I  " 

16x42      56 

39.8 

7107 

10661 

10996 

16x24 

•98 

38.3 

6840 

10260 

10511 

80    f  " 

17x42'     49 

40.0     7143 

10714 

11079 

17  x  30 

68 

39.2 

7000 

10500 

10766 

60  '  I  " 

16  x  42      75 

42.2     7536 

11304 

11639 

16  x  24 

133 

40.0 

7143  i    10814 

11065 

60   f  " 

17x42      66 

42.6 

7607 

11411 

11776 

17  x  30 

92 

41.4 

7393      11089 

11355 

60    |  " 

19x48      46 

43.7     7712 

11568     11982 

19x30 

75 

41.9 

7394      11091 

11401 

60    f  " 

21  x  48      40 

44.0  i    7765 

11647 

12122 

21x30 

61 

42.8 

7553 

11330      11686 

17*  iioo  is,* 

17  x  42      78 

25.9 

5332      $7999 

$8374 

17  x  30 

107 

25.2 

5250 

$7875 

$8151 

1  1  D       100    - 

19  x  48      54 

26.5'    5392        8089       8515 

19x30 

87 

25.6 

5270 

7905 

8225 

H.  P. 

100 

i   ti 

21x48      47 

26.6 

5413 

8119 

8607 

21x30 

71 

26.0 

5353 

8029 

8395 

so  i  " 

19  x  48      70 

28.2     5738'!      8608       9034 

19x30 

113 

27.1 

5577 

8365 

8685 

80    i  " 

21x48      60  '  28.4     5779        8669 

9157 

21x30 

92 

27.8 

5723 

8584 

8950 

80    i  " 

23x54      42    29.2     5874        8810 

9360 

23x36 

63 

'28.2 

5730 

8595 

9007 

80 

1     U 

24  x  54      38    29.4 

5914        8871 

9486 

24  x  36 

58 

28.4 

5780 

8670 

9131 

60 

i  " 

23x54      58    32.1 

6457        9686 

10236 

23  x  36 

89    30.7 

6256 

9384 

9796 

60 

1     U 

24x54      54    32.1 

6457        9686 

10301 

24  x  36 

82  1|  30.9 

6291 

9436 

9897 

60 

1    « 

26  x  54      46 

32.2     6477:i      9716 

10371 

26x42 

60 

31.4 

6387 

9581 

10072  ! 

60 

i  " 

27  x  60      38 

32.7  1    6503  i      9754 

10469 

27x42 

55 

31.7 

6376 

9565 

10101  i 

60 

i  " 

28x60      35    32.8 

6523        9784 

10560 

28x48 

45 

32.2 

6477 

9716 

10298  ! 

60 

i  (i 

30  x  60      31    33.0 

6563        9844 

10684 

30x48 

40 

32.4 

6517 

977& 

10406  I 

100 

•J  stroke 

15  x  36      79 

30.4 

6333      $9500 

$9825 

15x24 

121 

29.1 

6135 

$9203 

$9447  i 

100 

i   " 

16x42      59 

31.2 

6424        9635       9980 

16x24 

108 

29.4 

6125 

9187 

9447 

100 

i    « 

17x42      52 

31.4 

6465        9697 

10072 

17x30 

80 

30.0 

6250 

9375 

9651 

80 

1    a 

16x42      75 

32.9 

6774 

10160 

10505 

;  16  x  24 

132 

31.3 

6512 

9768 

10028 

80 

i    a 

17x42'    66 

33.2 

6835  [     10253 

10628 

17x30 

92 

32.4 

6750  ,!    10125 

10401 

80 

1    " 

19  x  48      46 

34.1 

6939 

1040S 

10834 

19x30 

74 

32.8 

6753      10129 

10449 

Continued  on       :     nr\ 
next  page. 

i     a 

21  x  48      40 

34.2 

6959 

10439 

10927 

21x30 

61 

33.2 

6835 

10252 

10618 

1  8                 Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines. 

LONG     STROKE     ENGINES 

SHORT     STROKE     ENGINES 

STEAM 

ENGINE 

COST  PER  YEAR 

COST   PRR  VEiR 

WATER 

OF  THE   POWER   NAMED 

ENGINE 

WATER 

OP  THE    POWER  NAMED 

A 

B                C 

D 

E 

F 

Q 

H                        I 

D                    E 

F 

c; 

H                         I 

L»J9 

Size 

and 

TOTAL 

Size 

and 

TOTAL 

NET 

PI 

,  4)  g  ja     Point 

Designa 

I 

Per 

Per  Hour 

For  Coal 

TOTAL,       Designa- 

1 

Per 

Per  Hour 

For  Coal       TOTAL, 

tion 

P        * 

1.  H.  P.       for  Net 

tion 

S  3 

I.  H.  P.       for  .vct 

HORSE             :  §        of 

C     3 

~     C 

per         Horse 

at  $8.00 

(  Interest 

0     S 

—  .5 

per    !    Hor<o 

at  $8.00      (Interest 

o> 

s 

1 

—    £ 

Hour       !'°wer 

on  cost  of 

| 

"o 

•§  * 

Hour 

Power 

on  cost  of 

POWER 

If  sr  Cut-off 

'     4>     O     t-i 

5 

£ 

1 

named 

per  Ton 

Engine 
included) 

5 

i 

1 

named 

per  Ton       En«ine 
included) 

£  =  o. 

In. 

In.    j 

I.I,.-            Lbs. 

In. 

In. 

i.i.-. 

Lbs. 

175 

60 
60 

^  stroke 
i    » 

19x48 
21x48, 

62 
54 

36.9 
37.0 

7509 

7529 

$11263 
11294 

$11689 
11782 

19x30 
21x30 

142 

83 

33.7 
35.6 

6938 

7330 

$10407    $10727 
10995      11361 

-»_    •      \-S 

60    I  " 

23x54 

37 

38.2 

7684 

11526 

12076 

23  x  36      56 

36.8 

7489 

11233      11645 

II.  p. 

60    i  "    i 

24x54 

34 

38.3 

7704 

11556 

12171 

24  x  36      52 

36.9 

7509 

11263      11724 

Concluded. 

100    I  stroke! 

14x36 

80 

36.2     7542,  $11312  $11579 

14x21    138 

34.6 

7271 

810906    $11106 

100    |   " 

15x36 

70 

36.5!    7604 

11406     11722 

15x24!  105 

35.3     7442 

11163      11400 

100  i  " 

16  x  42 

63 

36.7     7556 

11334     11669 

16x24;    92 

35.7     7437      11158      11409 

100  4  "  -  1 

17x42 

46 

37.4     7782 

11674     12039 

17x30      64 

36.7 

7646      11469      11735 

80   i  "  ! 

15x36 

87 

38.5 

8021 

12031     12347 

15x24'  133 

37.3 

7864 

11796 

12033 

80  '  1  " 

16x42 

65 

39.2 

8071 

12106     12441 

16x24    115 

37.6 

7833 

11750 

12001 

80    i  " 

17  x  42  ! 

58 

39.4 

8112 

12168     12533 

17x30      80 

38.6     8042 

12063 

12329 

80   |  " 

19  x  48  ! 

40 

40.3 

8201 

12301     12715 

19x30      65 

39.0!    8030 

12045 

12355 

60    £  " 

17  x  42 

78 

41.8 

8606 

12909 

13274 

17  x  30  ",  107 

40.61    8460 

12690 

12956 

60   |  " 

19  x  48  ' 

54 

43.0 

8750 

13125      13539 

19  x  30      87 

41.2     8483 

12724 

13034 

60    f  " 

21x48 

47 

43.1 

S77o 

13156     13631 

21x30 

71 

41.9 

8627 

12940 

13296 

200 

100 
100 

J  stroke 

i  " 

19x48 
21x48 

61 
53 

26.2 
26.3 

6070 
6116 

$9104 
9174 

$9530 
9662 

19x30 
21x30 

100 

81 

25.2 
25.6 

5930 
6024 

$8895 
9036 

$9215 
9402 

r^t  \J   \J 
TT      T> 

100 

i"' 

23x54 

37 

27.0 

6207 

9310 

9860 

23  x  36      56 

26.2 

6093 

9139        9551 

n.  r. 

80 

i  u 

21x48 

69 

28.0 

6512 

9767 

10255 

21  x  30    105 

27.0 

6353 

9529 

9895 

80 

i  " 

23x54 

48 

28.8 

6621 

9931 

10481 

23  x  36      72 

27.8     6465 

9697 

10109 

80 

i  " 

24x54 

44 

29.0 

6667 

10000 

10615 

24  x  36  '     66 

28.0     6512 

9768 

10229 

80 

1  " 

26x54 

37 

29.0 

6667 

10000 

10655 

26x42;>    48 

28.4     6605 

9907 

10398 

80 

i  " 

27  x  60 

31 

29.3 

6667 

10000 

10715 

27x42      45 

.  28.7     6598 

9897 

10433 

60 

i  " 

26x54 

53 

31.7 

7287 

10931 

11586 

26  x  42      69 

30.9     7186 

10779 

11270 

60 

i  " 

27  x  60 

43 

32.3     7341 

11011 

11726 

27x42 

63 

31.3     7195 

10793 

11329 

60 

i  " 

•28  x  60 

40 

32.4     7364 

11045 

11821 

28x48 

51 

31.3     7195 

10793 

11375 

60 

i  " 

30x60 

35 

32.6 

7409 

11114 

11954 

30  x  48 

45 

32.0 

7356 

11034 

11664 

100 

i  stroke  : 

15x36 

90 

29.9 

7119 

$10678 

$10994 

15x24 

138 

28.6 

6892 

$10338 

$10582 

100    I  " 

16x42 

68 

30.5     7176  i    10765     11110 

16x24    123 

28.8 

6857      10285 

10545 

100 

JL    u 

17x42 

60 

30.9 

7271 

10906     11281 

17x30      91 

29.7 

7072      10608 

10S84 

. 

100 

1     it 

19x48 

41 

31.6 

7349 

11023     11449 

19x30 

67 

30.4 

7153      10729 

11049 

80 

1     l( 

17x42 

76 

32.7     7694 

11541     11916 

17x30 

105 

31.7 

7547 

11320 

11596 

80    I  " 

19x48 

52 

33.7     7837 

11756     12182 

19  x  30 

85 

32.3 

7600 

11400 

11720 

80    £  " 

21x48 

46 

33.7     7837 

11756     12244 

21  x  30 

69 

32.8 

7718 

11677 

12043 

60 

1     « 

19x48 

71 

36.2     8419 

12629     13043 

19x30 

115 

34.4 

8094 

12141 

12461 

60    i  " 

21x48 

62 

36.3     8442 

12663     13151 

21x30 

94 

35.0 

8235 

12352 

12718 

60    i  " 

!  23  x  54 

43 

37.5     8621 

12931     13481 

23  x  36 

65 

36.1 

8395 

12592 

13004 

60    £  " 

24x54 

39 

37.7!    8667 

13000     13615 

24  x  36 

59 

36.3 

8442 

12663 

13124 

Continued  on 
next  page. 

60    i  " 

26x54 

34 

37.7 

8667 

13000     13655 

26x42 

45 

36.9 

8581 

12872 

13363 

Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines 

i 

19 

LONG     STROKE     ENGINES 

SHORT     STROKE 

ENGINES 

STEAM 

ENGINE 

WATER 

CIIST  ITK  -i  i:  \i: 

ENGINE 

WATER                    C°ST  PER  YEAR 

A 

B                < 

D                   E 

P 

G 

H                        I 

D                  E 

P 

G 

H 

I 

.    * 

Size 

and 

TOTAL 

!  Size 

and 

TOTAL 

NET 

•*5  B 

•  «  o~     Point 

Designa-      |_ 
tion         «  » 

,      Per  Hour     For  Coal       TOTAL, 
1.  H.  1.      for  Net 

'Designa-      |_ 
lion          §  s 

Per 

1.  11.  P. 

Per  Hour 

for  Net 

For  Coal 

TOTAL, 

HORSE 

-.-      <y                              Qf 

c    = 
-    c 

li 

per          Horse 
Hour       Power 

•tw.oo  r:rf 

•s  § 
|i 

per 

Horse 
Power 

at  $8.00 

(Interest 
on  cost  of 

a 

* 

X 

0) 
M 

POWER         *?.'.    L'ut-ott      s 

£  =  S 

i          > 

*      £ 

named 

Per  Ton       included) 

S 

S             P 

55       a, 

named 

per  Ton 

Engine 

In. 

In. 

Lbs 

Lbs. 

In. 

In. 

Lbs. 

Lbs. 

. 

200 

100    f  8troke 
100    f  " 

15x36      80 
16x42      59 

35.9 
36.8 

8548 
8659 

$12821   $13137 
12988      13323 

15x24    121 
16x24    105 

34.9 
35.2 

8410 
8381 

$12615 

12572 

$12852 
12823 

H.  P. 

100    |  "    :  17x42      52 

37.0 

8706 

13059      13424 

17x30      73 

36.1 

8595 

12892 

13158 

Concluded. 

SO    f  " 

16  x  42      74 

38.8 

9129 

13694     14029 

16x24    131 

37.2 

8857 

13285 

13536 

80    |  " 

17  x  42      66 

39.0 

9176 

13765     14130 

17x30      91    38.2 

9095 

13642 

13908 

80    f  " 

19  x  48      46 

39.8 

9256      13884     14298 

19x30      74    38.6 

9083 

13624 

13934 

60  !  f  " 

19x48      61 

42.5 

9884  j    14826     f5240 

19  x  30      99 

40.6 

9553 

14329 

14639 

60    f  " 

21  x  48      53 

42.7 

9930      14895     15370 

21x30      81 

!  41.3 

9718 

14577 

14933 

60    |  " 

23  x  54      37 

43.7 

10046  !    15069     15604 

23  x  36      56 

42.4 

9861 

14791 

15192 

99^  ISo 

/w^U 

4  stroke 
i  " 

19x48 
21x48 

69 
53 

25.8 
26.3 

6750 

(iSSl 

$10125 
10321 

$10551 
10809 

19x30 
21x30 

112    24.9 
92    25.3 

6588 
6706 

$9882 
10059 

$10202 
10425 

100 

i  " 

23  x  54 

41 

26.7 

6905 

10358 

10908 

23x36 

63    25.9 

6779 

10168 

10580 

H.  P.      100 

1  « 

24x54 

38 

26.7 

6905      10358 

10973 

24  x  36 

58    26.0 

6803 

10204 

10665 

80 

i  " 

23  x  54      54 

28.5 

737l'     11057 

11607 

23x36 

81    27.5 

7198 

10797 

11209  i 

80 

1    (( 

24  x  54      49 

28.6 

7397     11095 

11720 

24x36 

75    27.6 

7221 

10831 

11292  ! 

80 

i  " 

26  x  54      42 

28.7 

7422      11134 

11789 

26x42 

55    28.0 

7326 

10988 

11479 

80 

1    " 

27  x  60      35 

29.0 

7415  it    11122 

11837 

27x42 

50  I  28.3 

7318 

10978 

11514 

80 

1    « 

28  x  60  .    32 

29.0 

7415,    11122 

11898 

28x48 

41     28.6 

7386 

11078 

11660. 

60 

i  " 

27  x  60 

48 

31.9 

8156      12234 

12949 

27  x  42 

7o 

30.8 

7966 

11948 

.  12484 

60 

i  " 

28  x  60 

45 

32.0 

8181  1:    12273 

13049 

28x48 

57 

31.3 

8095 

12142 

12724  j 

60 

i  " 

30x60 

40 

32.2 

8233 

12349 

13189 

30  x  48 

50 

31.6 

8172 

12259 

12889 

100 

i  stroke 

16x42 

76 

30.3 

8021 

$12031 

$12376 

16x24 

138 

28.5 

7631 

$11446 

$11706 

100    i  " 

17  x  42      67 

30.4 

8047     12071 

12446 

17x30 

103    28.9 

7738 

11607 

11883 

100 

1      U 

19x48 

47 

31.3 

8189  !    12283 

12709 

19x30 

7.-» 

29.9 

7917 

11875 

12195 

80    £  " 

19x48 

59 

33.2 

8688      13029 

13455 

19  x  30 

(X,     32.1 

8494 

12741 

13061 

80 

tt-   " 

21x48 

51 

33.3 

8724      13086 

13574 

21  x  30 

78 

32,5 

8600 

12900 

13266 

80 

i   " 

23x54 

35 

34.2 

8845      13267 

13817 

23x36 

54 

33.1     8663 

12994 

13406 

60 

*    " 

21x48 

70 

35.7 

9340  i    14010 

14498 

21  x  30 

106 

'  34.5 

9129 

13693 

14059 

60   I  " 

23x54 

48 

37.1 

9595      14392 

14942 

23x36 

73    35.6 

9314 

13971 

14383 

60 

i    « 

24  x  54      44 

37.3 

9658,     14487 

15102 

24  x  36 

67  ;  35.8     9360 

14040 

14501 

60 

*   " 

26x54:    38 

37.3 

9658  ,    14487 

15142 

26x42 

50    36.2     9471 

14196 

14687 

60 

i    « 

27x60 

31 

37.8 

9665      14497 

15212 

27  x  42 

41 

37.2 

9621 

14431 

14967 

100 

f  stroke 

15  x  36 

90 

35.6 

9536   $14304 

$14620 

15  x  24 

136 

34.5 

9349 

$14023 

$14260 

100 

f   " 

16x42 

67 

36.3 

.  9609      14413 

14748 

16x24 

118    34.6     9262 

13S93 

14144 

100 

f   " 

17  x  42      59 

36.5 

9662      14493 

14858 

17x30 

81 

35.7 

9559 

14338 

14604 

100 

f   « 

19  x  48 

41 

37.2 

9733      14699 

15113 

19x30 

66 

36.1     9553 

14329 

14639 

80 

1   " 

17x42 

74 

38.6 

10218      15326 

15691 

17  x  30 

103 

37.7 

10095 

15142 

15408 

Continued  on 
next  page. 

80 

19x48 

51 

39.5 

10334      15501 

15915 

19  x  30 

83 

38.3  10141 

15212 

15522 

2O                  Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines. 

LONG 

STROKE     ENGINES 

SHORT    STROKE    ENGINES 

STEAM 

ENGINE 

COST  PER  YEAR 

COST  PER  YEAR 

WATER 

OF  THE   POWER   NAMED      1 

EXGIXE 

WATER 

OF  THE  POWER  X.IMEII 

A 

B 

c 

D 

E 

F 

a 

HI                          D                   B 

F 

o 

H                       I 

4J 

Size 

and 

TOTAL 

1  Size 

and 

TOTAL 

NET 

««1 

o  5  —     Point 

Designa 

b 

5, 

Per 

Per  Hour 

For  Coal 

TOTAL,       Designa-      g. 

Per 

Per  Hour 

For  Coal      TOTAL, 

W-—              J.V1141. 

c  -•  c 

tion 

c  S 

I.  H.  P.       lor  Net 

tion 

3  S 

I.  H.  P. 

for  Net 

HORSE 

of 

C     3 

^      C 

per          Horse 

at  $8.00      <Intcrest 

0     3 

3  .= 

per 

Horse 

at  $8.00  ;    (Intere8t 

. 

-  £•  ? 

2 

j 

E  5  9  _ 

S 

0 

•=    S 

Hour 

Power 

1 

•g 

-3  * 

Hour 

Power 

POWER 

*•=.?  Cut  off 

1 

g 

02 

>• 

3 

named 

per  Ton 

Engine 

A 

c 

w 

1 

named 

per  Ton 

Engine 

£  S  £ 

PC 

included) 

M 

included) 

i.  =  2. 

In. 

In 

l.l.s 

[.I.-. 

In 

In. 

Lbs. 

Lbs. 

225 

80 
60 

i  stroke 

f  " 

21x48 
19x48 

45 
69 

39.5 
41.9 

10334 

10962 

$15501 
16443 

$15976 
16857 

21x30 
19x30 

68 
112 

38.6 
40.1 

10212 

10612 

$15318    $15674 
15918      16228 

ii.  P. 

21x48 

60 

42.0  109SS 

16483 

16958 

21x30      91 

40.7 

10776 

16164      16520 

Concluded.              60     £    ' 

23  x  54 

41 

43.3   11198 

10797 

17332 

23  x  36      63 

41.8 

10930 

16396      16797 

II   60 

8     U 

•2  1  .  .M 

38 

43.4   11224 

1(1836 

17436 

24  x  36      58 

42.0 

10988 

16482 

16932 

OKA     100 

i  stroke 

21x48 

67 

25.7 

7465' 

'$11198 

$11686 

21x30 

102    25.0 

7353 

$11029 

$11395 

2131)   !ioo 

i   " 

23x54 

46 

26.5 

7615      11422     11972 

23x36 

70    25.6 

7442 

11163 

11575 

100 

i  " 

24x54 

42 

26.5 

7615      11422     12037 

24x36 

64 

25.7 

7465 

11198 

11659 

II.  P.        IOQ 

i  " 

26  x  54 

36 

26.4 

7586      11379 

12034 

26  x  42      47    25.9 

7529 

11294      11785 

100 

i  " 

27  x  60 

30 

26.7 

7586      11379 

12094 

27x42      43    26.2 

7529 

11294      11830 

80 

i  " 

23  x  54 

60 

28.2 

8102      12153 

12703 

23x36      90    27.2 

7907 

11860 

12272 

80 

i  " 

24x54 

55 

28.3 

8131      12197 

12812 

24x36      S3    27.4 

7965 

11947 

12408 

80 

i  " 

26x54 

46 

28.4 

8161      12241 

ll^'.T, 

26  x  -i-2 

61     27.8 

8081 

12122 

12613 

80 

i  " 

27x60 

38 

28.8 

8182      12273 

12988 

27  x  42      56    28.0 

8023 

12034 

12570  '• 

80 

i  " 

28x60 

36 

28.8 

8182      12273 

13049 

28x48      45    28.4 

8148 

12222 

12804  ' 

80 

i  " 

30x60 

31 

29.0 

8239      12358 

13198 

30x48 

39    2S..6 

8218 

12327 

12957  ; 

60 

i  " 

28x60 

50 

31.6 

8979      13469 

14245 

28x48 

63 

31.0 

suns 

13362 

13944 

60 

i  " 

30  x  60 

44 

31.9 

'.KM;:; 

13594 

14434 

30  x  48      56 

31.2 

8966 

13448 

14078  ! 

100 

i  stroke 

17x42 

75 

30.0 

8824 

$13235 

$13610 

17x30    114 

28.8 

8571 

$12857 

$13133 

100 

i   " 

19x48 

52 

30.9 

S'.is:; 

13474 

13910 

19x30      84    28.8 

S471 

12706 

13026 

100 

i   " 

21x48 

43 

31.3 

9(199 

13648     14136 

21x30      73    29.9 

8788 

18182 

13548 

80 

i   " 

19x48 

66 

32.9 

9564 

14346     14772 

19x30    106    31.4 

9235 

13852 

14172 

80 

i   " 

21x48 

57 

33.0 

9593      14390 

14878 

21x30 

87    32.1 

9435 

14125 

14491 

80 

i   i( 

23x54 

39 

33.0 

9483      14224 

14774 

23x36 

60 

32.9 

9560 

14340 

14752 

80 

i   " 

24x54 

36 

33.0 

9483      14224 

14839 

24x36 

55 

32.9 

9560 

14340 

14801 

60 

k   " 

23x54 

53 

36.6 

10515  :     15773 

16323 

23x36 

81 

35.1 

10197 

15295 

15707 

60 

i    " 

24x54 

49 

36.9 

10613      15920 

16535 

24  x  36      74 

35.4 

10291 

15436 

15897 

60 

4  " 

26x54 

42 

36.9 

10613      15920 

16575 

26x42      56 

36.0 

10465 

15698 

16189  1 

60 

k  " 

27  x  60 

34 

37.4 

10625      15938 

16653 

27x42      50 

36.4 

10460 

15690 

16226 

60 

i  " 

28x60 

32 

37.4 

10625      15938 

16714 

28  x  48      41 

36.8 

10563 

15845 

16427  ! 

100 

1  stroke 

16x42 

74 

35.9 

10559 

$15838 

$16173 

16x24    131     34.4 

10238 

$15357 

$15608  ! 

lun    £  « 

17x42 

66 

36.2 

10647      15971 

16336 

17x30      91 

35.4 

10536 

15SO-1 

16070  ! 

100  i  f  " 

19x48 

45 

37.0 

10756 

16134 

16548 

19  x  30      74 

35.7 

10494 

15741 

16051 

80    £  « 

19  x  48 

57 

39.1 

11366 

17049 

17463 

19  x  30      93    37.8 

11113 

16669 

16979 

80    |  « 

21x48 

50 

39.2   11395 

17093     17568 

21x30      75    38.3 

11259 

16888 

17244 

80    I  " 

23x54 

35 

39.9   11463      17195;    17730 

23x36      52    39.0 

11337 

17005 

17406 

60   |  " 

21x48 

67 

41.6   12093      18140     18615 

21x30 

102 

39.1 

11360 

17040 

17396 

60   I  " 

23x54 

46 

42.9   12328 

18491     19026 

23x36      70    41.3 

12000 

18000 

18401 

60  i  i  " 

24x54 

42 

43.1   12385:     18578     19178 

24  x  36      64    41.6 

11x1113 

18139 

18589 

60 

f   " 

26  x  54 

36 

43.0 

12356'     18534     19172 

26x42'    47'  42.1 

12238 

18357 

18835  I 

60 

*   " 

27x60 

30 

43.4 

12330;     18494     19191 

27  x  42      43    42.6 

12241 

18362 

18885 

Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines.                 21 

LONG    STROKE    ENGINES 

• 

SHORT     STROKE     ENGINES 

STEAM 

ENGINE 

WATER 

COST  PEK  YEAR 

OF  THE   POWER   NAMED 

ENGINE 

WATER 

COST  PER  YEAR 

OF   THE  POWER   NAMED 

A 

B 

c 

u 

E 

F 

o 

11                              I 

D 

E 

F                 0 

H                      I 

Size 

and 

TOTAL 

Size 

and 

TOTAL 

NET 

Point 

Designa 

a 

Per 

Per  Hour 

For  Coal      ToTAL> 

Designa 

Per 

Per  Hour 

For  Coal 

TOTAL, 

o  &  c 

tion 

2    *> 

I.  U.  P. 

for  Net 

tion 

=  3 

I.  H.  P. 

for  Net 

HORSE 

of 

|| 

per 

Horse 

at  $8  00      oncost"  f 

•B   a 

per 

Horse    i:  at  $8.00 

(Interest 

w 

POWER 

§  v  a 

if* 

V  &  I* 
•Pal 

Cut-off 

S 
5 

i 

1 

Hour 

Power 
named 

Engine 
per  Ton      included) 

1 

S 

<» 

i* 

Hour 

Power 
named         per  Ton 

Engine 
included) 

In. 

In. 

Lbs. 

Lbs. 

In. 

In. 

u*. 

Lbs. 

275 

100 
100 
100 

i  stroke 
i   " 

1      U 

21x48 
23x54 
24x54 

74 
51 
46 

25.5 

26.2 
26.2 

8154 

8295 

8282  ' 

$12231 
12443 
12422 

$12719 
12993 
13037 

21x30 
23x36 
24x36 

112 

77 
71 

24.8 
25.4 
25.5 

8023 
8116 
8163 

$12034 
12174 
12244 

$12400 
12586 
12705 

H.  P. 

100 

i   " 

26x54 

40 

26.2     8282'     12422     13077 

26x42 

52 

25.7 

8218 

12327 

12818 

100 

i  " 

27  x  60 

33 

26.4     8250 

12375     13090 

•  27x42      47 

25.9 

8187 

12280 

12816 

100 

i  " 

28x60 

30 

26.5 

8281 

12422     13198 

28  x  48      39 

26.1 

8250 

12375 

12957 

80 

i  " 

24  x  54 

61     28.0     8851 

13277 

13892 

24x36      88 

27.2 

8651 

12977 

13438 

80 

1   u 

26x54 

51     28.2     8914 

13371     14026 

26x42      67 

27.5 

8794 

13190 

13681 

80 

i  " 

27  x  60  i,    42     28.5     8906 

13359     14074 

27x42      61 

27.8     8787 

13181 

13717 

80 

i  " 

28  x  60      39  '  28.6     8937 

13406     14182 

28x48      50 

28.1 

8882 

13323 

13905 

80 

1    " 

30x60;     35    28.7 

9084 

13625     14465 

30  x  48      43 

28.4 

8988 

13483 

14113 

60 

i  " 

30x60 

48 

31.6 

9875 

14813 

15653    30x48"     62 

30.9 

9767 

14651 

15281 

100 

4  stroke 

19x48 

57 

30.4 

9721 

$14581   $15007 

19  x  30      92 

29.4 

9472 

$14208 

$14528 

100 

1       u 
2 

21  x  48 

47 

30.9     9881 

14821 

15309 

21  x  30      80 

29.5 

9553 

14329 

14695 

100 

1      U 

23x54 

34    31.6     9989 

14984 

15534 

23  x  36      52 

30.5 

9744 

14616 

15028 

80 

1      U 

19x48 

73  i  32.6  ;  10424 

15636 

16062 

19x30    117 

31.2 

10094 

15141 

15461 

80 

1      U 
2 

21x48 

63    32.7  10456 

•15685 

16173 

21x30      96 

31.7 

10240 

15360 

15726 

80 

1    (( 

23x54 

43 

33.7  10652'     15978 

16528 

23  x  36      66 

32.5 

10384      15576 

15988 

80 

1     (i 

24x54 

40 

33.8 

10684      16026 

16641 

24x36 

60 

32.7 

10465      15697 

16158 

60 

i  " 

23x54 

58 

36.3  11474     17211 

17761 

23x36 

89 

34.8 

11130 

16695 

17107 

60 

1    » 

24x54 

54 

36.4   11502      17253 

17868 

24x36 

82 

35.0 

11151 

16726 

17187 

60 

1    (( 

26x54 

46 

36.5    11537      17306 

17961 

26  x  42      61 

35.6   113*4 

17076 

17567 

60 

1     U 

27x60 

38 

37.1   11594      17391     18106 

27  x  42      55 

36.0  11379 

17069 

17605 

60 

1    « 

28x60 

35 

37.2  11625      17438 

18214 

28  x  48      45 

36.4 

11506 

17259 

17841 

60 

i  " 

30x60 

31 

37.4  11687 

L7531 

18371  j 

30x48      39 

36.9 

11664 

L  741t6 

18126 

300 

100 
100 

X  stroke 
i    a 

23x54 
24x54 

55 
50 

26.0 

26.0 

8965 
8965 

$13448 
13448 

$13998 
14063 

23  x  36 
24x36 

84 

77 

25.2 
25.3 

8791 

8825 

$13186 
13238 

$13598 
13699 

100    1  " 

26x54 

43 

26.1 

9000      13500     14155 

26x42 

56 

25.5 

8895 

13343 

13834 

.    1  .     ' 

100 

1    " 

27x60 

36 

26.3 

8966      13449     14164 

27x42 

52 

25.7 

8839 

13259 

13795 

100 

i    « 

28  x  60 

33 

26.3 

8966  ;    13449     14225 

28x48 

42 

25.9 

8931      13397 

13979 

so  i  " 

27  x  60 

46 

28.3 

9648  j    14472     15187 

27x42 

67 

27.5 

9483 

14224      14760 

80  !  i  " 

28x60 

43 

28.4 

9625      14438      15214 

28  x  48 

54 

27.9 

9621      14431      15013 

80 

i  " 

30  x  60 

38 

28.5 

9716 

14574 

15414 

30x48 

47 

28.2 

9724 

14586 

15216 

100 

i  stroke 

19x48 

62 

30.2 

10535 

$15802 

$16228 

19x30 

101 

28.9 

10200 

$15300 

$15620 

100    *  " 

21x48 

51 

30.5 

10640      15959     16447 

21x30 

86 

29.4 

10377 

15565 

15931 

. 

100 

4   " 

23x54 

37 

31.3 

10793      16190 

16740 

23x36 

56 

30.3 

10570 

15855 

16267 

Continued  on 
next  page. 

100 

i   " 

24x54 

34 

31.3 

10793 

16190 

16805    24x36 

III 

52 

30.4 

10605 

15907 

16368 

22                  Tables  showing  Power,  &c.,  of  Non-Condensing  Stationary  Steam  Engines, 

LONG 

STROKE     ENGINES 

SHORT     STROKE 

ENGINES 

STF.A1U 

ENGINE 

WATER 

COST  PER  TEAR 

OF  THE    POWER  NAMED 

ENGINE 

WATER 

COST  PER  YEAR 
OF  THE   POWEH  NAMED 

A                         B                C 

D 

E 

F                 0 

H 

i 

I) 

E 

F 

• 

H 

i 

*9 

Size 

and 

TOTAL 

Size  and 

TOTAL 

NET 

Point 

Designa-      S, 

Ppr 

Per  Hour 

For  Coal 

TOTAL, 

Designa 

a. 

Per 

Per  Hour 

For  Coal 

TOTAL, 

lion 

K        -j 

1.  H.  P.       for  Net 

tion 

§  S 

1.  B.  P. 

for  Net 

HORSE                        of 

II  = 
POWER         Iff   Cut-°ff 

B 
1 

49 

M 

£ 

Hpvoluti 
Min 

per 
Hour 

Horse 
Power 
named 

at  $8.00 
per  Ton 

on  cost  of 
Engine 
included) 

6        1 
£        53 

Kovoluti 

Min 

per 
Hour 

Horse 
Power 
named 

at  $8.00 
per  Ton 

on  cost  of 
Engine 
included) 

In. 

In. 

Lbs.           Lbs. 

In.        In. 

I.l.s 

Lbs. 

OAA      80  £stroke 

$00    so;  i" 

21  x  48 
23x54 

68 
47 

32.4 
33.3 

11302 
11483 

$16953 
1  -•»  i 

$17441 
17774 

21  x  30 
23x36 

104 

72 

31.3 
32.2 

11047 
11163 

$16570 
16744 

$16936 
17156 

80    *  " 

24  x  54 

43 

33.4  11517 

17276 

17891 

24x36 

66    32.4 

11303 

1  ii'.Ci  t 

17415  i 

H.  P.          80 

i   <( 

26  x  54 

37 

33.4 

11517 

17276 

17931 

26x42 

48 

32.8 

11442 

17163 

17654  ! 

Concluded.             QQ 

i    a 

27x60 

30 

33.9 

11557 

17335 

18050 

27x42 

44 

33.1 

11414 

17121 

17657  j 

i;n    i  « 

26x54 

50 

36.2 

12437 

18655 

19310 

26  x  42 

67 

35.1 

12244 

18366 

18857 

60 

i    11 

27x60 

41 

36.8  12545*    18818 

19533 

27  x  42 

60 

35.6 

12278 

18417 

18953 

60 

*   " 

28x60 

38 

36.9 

12580 

IS.Mi'.t 

19645 

28x48 

49 

36.1 

12448 

18672 

19254 

60    I  " 

^0x60 

34 

37.1 

12648 

18972 

19812 

30x48 

42 

36.5 

125S6 

18879 

19509 

350 

100 
100 

i  stroke 

24x54 
26  x  54 

58 
50 

25.7 

25.7 

10340 
10339 

$15510 
15509 

$16125 
16164 

24x36 
26x42 

90 
66 

25.0 
25.2 

10174 
10256 

$15261 
15384 

$15722 
15875  : 

100 

i    " 

27x60 

42 

25.9 

10301 

1  :>•».->  2 

16167 

27  x  42 

60    25.4 

10218 

15328 

15864 

H.  P.        100 

i    11 

28x60 

39 

25.9 

10301 

15452 

16228 

28x48 

49     25.6 

10298 

15447 

16029 

|100 

i    a 

<  : 

30  x  60 

34 

26.1 

10381 

15571 

16411 

30  x  48 

43     25.8 

10494 

15740 

16370  : 

80 

i" 

30x60 

44 

i  28.2 

11216 

16824 

17664 

30x48 

55 

27.7 

11144 

16716 

17346 

100 

k  stroke 

19x48 

72 

29.7 

12087 

$18131 

'$18557 

19  x  30 

117 

28.5 

11730 

$17595 

$17915 

, 

100 

1   it 

21x48 

60 

30.0 

12209 

18314 

1  -^IIL' 

21  x  30 

100    28.7 

11812 

17718 

18084  ' 

100 

*    " 

23x54 

44 

30.9 

12431 

18647 

I'.i  197 

23x36 

66 

29.8 

12130 

18195 

18607 

100 

*   " 

24  x  54 

40 

30.9 

12431 

18647 

19262 

24x36 

61 

l".'.!> 

12163 

18244 

18705  ! 

•  80 

4  " 

23  x  54 

55 

32.8 

13195 

19793 

20343 

23x36 

83    31.8 

12942 

19413 

19825 

80 

i  a 

24x54 

50 

33.0 

13276 

19914 

20529 

24x36 

76    32.0 

13023 

19534 

19995 

80 

i  " 

26x54 

43 

33.0 

13276 

19914 

20569 

26x42 

56    :-!2.4 

13186 

19779 

20270 

80 

i    a 

27  x  60 

36 

33.3 

13245 

19867 

20582 

27x42 

51 

32.7 

13155 

19733 

20269 

80 

i    11 

28  x  60 

33 

33.3 

13245 

I9S67 

20643 

28x48 

42    32.9 

13236 

19853 

20435 

60 

*'" 

27  x  60 

48 

36.2 

14398 

21597 

22312 

27x42 

70    34.9 

14040 

21060 

21596 

60 

*    " 

28x60 

45 

36.3 

14438 

21656 

22432 

28  x  48 

57    35.5 

14201 

21302 

21884 

60 

1      U 

30  x  60 

39 

36.6   1467H 

22006 

22846 

30x48 

49    36.0 

14483 

21725 

22355 

11 

I 

I.H.P p/7  //f>/t/: 


Hs 

llAGRAM    No.    1    is    intended    to    show,    by    inspection,    the    number    of    pounds    of    water 
1  required  per  hour  for  one  Indicated  Horse   Power,   at   different    steam    pressures    and    points 
of  cut-oft'. 

In  this  Diagram  the  vertical  lines  drawn  through  .0,  .20,  .30,  etc.,  show  the  proportion  of 
stroke  at  which  it  is  assumed  that  the  steam  is  cut-off",  in  various  cases — the  figures  expressing 
decimally  that  proportion. 

The  horizontal  lines  drawn  through  70,  60,  50,  etc.,  show  the  number  of  pounds  of  water 
required  per  hour  for  one  Indicated  Horse  Power. 

The  curved  lines  A,  B,  C,  D  and  E  refer  respectively  to  the  steam  pressures  named  : 

The  curve  A  being  the  line  for  pressure  of  25  Bbs. 

it  |;  it  it  tt  |n      .. 

"  C  "  "  "  60     " 

D  "  80     " 

E  "  "  100     " 

To  find  from  Diagram  No.  1  the  number  of  pounds  of  water  per  Indicated  Horse  Power  per 
hour  at  a  pressure  of  steam  and  proportion  of  cut-off  named,  suppose  the  pressure  to  be  60  Bbs. 
and  proportion  of  cut-off'  .30: 

Find  the  intersection  of  the  vertical  line  passing  through  .30  with  the  curved  line  C  representing 
60  ft>s.  steam  pressure.  It  will  be  seen  that  a  horizontal  line  drawn  through  this  intersecting  point 
will  pass  through  41,  in  the  vertical  line  showing  pounds  of  water,  showing  that,  for  a  steam 
pressure  of  60  ft>s.,  with  proportion  of  cut-oft'  .30,  the  pounds  of  water  per  Indicated  Horse  Power 
per  hour  is  41. 

It  will  be  seen,  on  examination,  that  the  point  of  cut-off,  most  economical  in  water,  varies  with 
the  pressure  of  steam. 

When  the  cylinder  exceeds  one  cubic  foot  capacity,  the  pounds  of  water  will  be  somewhat 
less  than  is  shown  by  the  Diagram. 

The  lowest  point  of  each  curve  shows  the  least  number  of  pounds  of  water  and  the  most 
economical  point  of  cut-off  for  each  steam  pressure. 

The  curves  A,  B,  C,  D  and  E  have  been  obtained  from  a  large  number  of  experiments  made 
with  a  small  engine,  the  experiments  with  each  pressure  furnishing  a  series  of  points  through 
which  a  curve  was  drawn. 

In  Diagram  No.  2  the  curves  D  and  F  are  presented  to  show  the  difference  in  pounds  of  water 
when  the  cylinder  is  less  than  one  cubic  foot  capacity,  and  when  the  cylinder  is  greater  than  ten 
cubic  feet  capacity ;  a  steam  pressure  of  80  Bbs.  being  used  in  both  cases.  The  curves  H  and  G  are 
presented  to  show  the  number  of  pounds  of  water  which  would  be  required  by  calculation  according 
to  Mariotte's  law  and  the  well-known  tables  of  specific  volumes.  Curve  H  being  the  theoretical 
curve  where  there  are  no  clearances  and  the  curve  G  the  corresponding  curve  when  the  capacity 
of  clearances  and  ports  equals  one-twentieth  of  the  piston  development. 


'24  Explanation    of  Diagrams. 

There  are  four  conditions  which  influence  the  economy  of  a  non-condensing  steam  engine, 
viz:  1st — The  steam  pressure;  2d — The  amount  of  expansion;  3d — The  speed  of  revolution,  and  4th — The 
size  of  the  cylinder.  The  relative  and  actual  value  of  each  of  these  has  been  determined  by  careful 
experiment.  By  combining  together  the  facts  thus  obtained,  the  cost  of  the  Indicated  Horse  Power 
has  been  ascertained  in  pounds  of  water  per  hour  for  any  desired  steam  pressure,  point  of  cut-off, 
speed  of  revolution  or  size  of  engine.  Such  results,  for  the  regular  sizes  of  the  engines  manufactured 
at  The  Novelty  Iron  Works,  are  presented  in  the  tables  on  page  7  el  seg.,  in  columns  F  and  F,  headed 
"Water  per  Indicated  Horse  Power  per  hour."  The  tables  are  particularly  useful  in  showing  the 
exact  value  of  several  of  the  methods  of  producing  economy  of  steam. 

The  economy,  due  to  an  increase  in  the  size  of  the  engine,  is  shown  in  the  tables  by  comparing 
different  horse  .powers,  produced  under  like  conditions,  and  necessarily,  therefore,  in  different  sized 
engines.  It  will  be  found,  however,  by  selecting  any  particular  horse  power,  that  the  highest  steam 
pressures  and  revolutions  and  shortest  points  of  cut-off  mentioned  are  those  which  show  the  greatest 
economy  of  steam.  When  these  three  conditions  are  all  favorable,  at  the  same  time,  the  maximum 
economy  is  obtained,  but  when  one  or  more  only  is  favorable,  the  results  are  so  modified  as  often  to 
appear  contradictory.  For  instance,  the  short  stroke  engines  are,  in  all  cases,  a  little  more  economical 
than  the  corresponding  long  strokes,  and  the  small  engines  of  each  class  are  more  economical  than 
the  large  ones,  in  all  cases  where  the  steam  pressures,  points  of  cut-off'  and  power  developed 
are  the  same;  for,  although  the  smaller  engine,  at  the  same  speed,  would  be  less  economical,  at 
the  higher  speeds,  necessary  to  produce  the  same  power,  the  gain,  due  to  the  high  speed,  overbalances 
the  loss  due  to  the  smaller  size  of  cylinder,  as  is  shown  all  through  the  tables. 

Selecting  for  more  particular  comparison,  60  Horse  Power,  on  page  12,  we  find  that  using  a 
steam  pressure  of  60  Ibs.  cut-oft'  at  one-quarter  of  the  stroke,  in  a  17x42  engine,  running  49 
revolutions,  the  cost  of  the  Indicated  Horse  Power  is  83.9  ibs.  of  water  per  hour;  while,  by  using 
100  Ibs:  steam  pressure,  cut  oft'  at  one-half  of  the  stroke,  in  a  10  x  24  engine,  running  94  revolutions, 
•the  cost  is  only  31.6  ibs.  of  water  per  hour.  So  likewise,  the  same  power  can  be  obtained  in  a 
9x24  engine,  at  102  revolutions,  using  100  fibs,  steam  pressure,  cut  off"  at  three-quarters  of  the  stroke, 
more  economically  than  it  can  in  a  14x36  engine  at  55  revolutions,  using  60  ibs.  steam  pressure, 
cut  oft'  at  one-half  of  the  stroke.  In  these  cases,  the  higher  steam  pressure  and  revolutions  overbalance 
greatly  the  losses  due  to  the  less  expansion  and  smaller  engine. 

J  and  K  (No.  3)  are  Indicator  Diagrams,  which  are  intended  to  show  the  comparative  value 
of  regulating  speed  by  the  throttle  or  by  the  cut-oft'.  The  diagrams  are  of  the  same  area  and 
were  taken  from  the  same  engine.  The  pressure  in  the  steam  pipe  was  80  ibs.  above  the 
atmosphere,  in  both  cases. 

Diagram  J  was  taken  with  the  throttle  partially  closed  and  the  steam  cut  off  in  the  cylinder 
by  the  lap  of  the  main  valve,  at  seven-eighths  of  the  stroke.  • 

Diagram  K  was  taken  with  the  steam  cut  oft'  at  one-fourth  of  the  stroke,  by  an  independent 
valve.  It  has  been  usual  to  compare  such  diagrams  by  assuming  that  there  is  used,  in  each  case, 
only  a  cylinder  full  of  steam  of  the  terminal  pressure.  This  assumption  has  been  found  to  be 
incorrect  in  practice.  We  may,  however,  compare  the  two  systems  of  working  by  referring  to 
the  curves  on  Diagram  No.  1.  The  initial  pressure  of  Indicator  Diagram  J  is  53  ibs.,  and  as  the 
point  of  cut-oft'  is  seven-eighths  of  the  stroke,  by  referring  to  No.  1  we  find,  at  the  point  a,  that  an 
engine,  working  under  these  conditions,  requires  56  Ibs.  of  water  per  indicated  horse  power  per  hour. 
The  initial  pressure  of  diagram  K  is  80  ibs.,  and  the  point  of  cut-oft'  being  one-fourth  of  the  stroke, 
we  find  at  b,  in  like  manner  as  before,  that  the  water  required  is  only  35  Ibs.  per  hour. 


flplpEv  S' .-  ;Ej|]M^»  : !  1  ^;4feJJilli 

:3<%p.;i"Ji,  ':r.'i:'-|:.':-'i  ''•L^»r]l:;::'"'-;f __•:.••&]•••    J"'';.i..'.'.1^..'.Jrt^J:        ]         •   '     '      :      '     : 
';fV;.  ,••!  '^''''^''W^Wi'ffli^Wt-'^J^^^^ 


,.       > -..j, 

f 


HE  engraving  represents  one  of  the  Non-Condensing  Stationary  Steam  Engines  built  at  The 
^Novelty  Iron  Works,  New  York. 
^H?  The  bed-plate  of  the  engine  is  of  the  style  introduced  many  years  ago  by  The  Novelty  Iron 
"Works,  and  has  since  been  extensively  copied  by  other  manufacturers.  It  may  be  described  as  a 
strong  cast-iron  box,  one  end  of  which  is  so  constructed  as  to  form  a  cylinder  head  and  the  other  a 
pillow  block  for  the  main  shaft.  The  main  slides  also  form  part  of  the  same  casting  as  do  also 
the  strong  legs  and  broad  feet  upon  which  the  frame  is  supported.  This  bed-plate  has  the  advantages 
that  the  metal  is  disposed  directly  in  the  line  of  the  strains,  and  neither  the  cylinder,  main  slides 
or  pillow  block  can  work  loose  or  get  out  of  proper  adjustment.  The  legs  upon  which  the 
frame  rests  are  put  under  the  slides  and  under  the  shaft,  which  is  an  additional  security  against  any 
springing  of  the  frame  from  the  oblique  strains  brought  to  bear  at  these  points  by  the  connecting  rod 
and  crank.  The  cylinder  being  attached  at  only  one  end  to  the  bed-plate  is  free  to  expand  when  heated 
without  any  alteration  of  shape — the  outer  end  simply  sliding  over  a  small  stationary  standard  which 
carries  part  of  the  weight. 

Tlie  steam  is  admitted  to  and  from  the  cylinder  by  a  plain  slide  valve,  so  arranged  that  the 
cylinder  ports  are  very  short  and  direct,  and  the  amount  of  steam  required  to  fill  the  clearance  and  port 
is  much  less  than  in  any  other  arrangement  in  use. 


'26  TSTon-Condensing    Stationary    Steam    Engine. 


The  cut-oft'  consists  of  two  plates  sliding  on  the  back  of  the  main  valve  and  operated  by  a  separate 
eccentric.  This  cut-oft'  is  either  set  at  a  fixed  point,  in  the  usual  way,  or  made  so  that  it  can  be  adjusted 
by  hand,  from  zero  to  seven-eighths  stroke,  by  simply  turning  the  cut-off'  valve  stem;  Preferably, 
however,  the  adjustment  is  made  by  the  governor  through  a  simple  arrangement  which  we  will 
try  and  make  understood  Avithout  illustrations.  The  cut-oft'  is  varied  by  drawing  together  or 
spreading  apart  the  cut-oft'  plates.  To  accomplish  this  by  the  governor,  the  plates  are  operated  by 
separate  rods  which  pass  outside  the  chest  and  connect  to  the  ends  of  a  small  double-ended  vertical 
lever,  the  center  of  which  receives  motion  from  the  cut-oft'  eccentric.  The  double-ended  lever  has 
attached  to  it  a  horizontal  arm,  which  is  operated  to  adjust  the  plates  by  a  vertical  movement  derived 
from  an  adjusting  screw  on  the  governor. 

The  governor  is  driven  by  gear  in  the  simple  manner  shown,  so  as  to  be  reliable  in  its  action, 
and  is  what  is  ordinarily  called  a  "  mill  governor."  The  governor  balls  have  a  very  slight  movement, 
which  simply  causes  a  disk  on  the  adjusting  screw  mentioned  to  be  clutched  to  the  wheels  operating 
the  governor  in  such  a  manner  that  the  screw  is  turned  in  one  direction  by  the  engine  when  the 
balls  rise,  and  in  the  other  direction  when  the  balls  fall — thereby  adjusting  the  cut-oft'  plates,  by  the 
power  of  the  engine,  the  instant  the  speed  changes.  The  screw  stops  when  the  proper  speed 
is  restored,  and  the  cut-oft'  plates  are  held  by  it,  in  a  fixed  position,  until  a  further  change  of  speed 
takes  place. 

The  advantages  of  this  form  of  governor  cut-oft'  are,  that  it  is  simple  in  construction,  positive 
and  reliable  in  its  operation,  and,  unlike  any  common  governor,  gives  exactly  the  same  speed 
throughout  the  full  range  of  power  and  steam  pressure. 


ines  Recommended  for  Given  Powers. 


HE  tables  on  page  7  el  seq.,  show  conclusively  that  any  particular  horse  power  can  be  obtained 
'in  a  variety  of  ways  in  either  of  a  large  number  of  engines  of  different  sizes.  All  the  cases 

are  entirely  practical  if  the  engines  are  especially  designed  to  operate  under  the  conditions 
stated,  but  there  are  few  instances  in  which  it  would  be  desirable  to  use  the  extremes  mentioned. 
The  proper  size  of  an  engine,  and  the  conditions  under  which  it  is  to  be  run,  must  be  determined 
by  the  requirements  of  each  particular  case. 

One  great  difficulty  in  fixing  the  proper  size  of  an  engine  is  to  know  what  power  is  actually 
required  by  the  purchaser.  'Too  often  this  is  underrated,  whence  for  safety  manufacturers  have 
been  in  the  habit  of  furnishing  an  engine  large  enough  for  all  contingencies,  and  therefore,  in 
many  cases,  too  large  to  do  the  work  economically.  We  believe  that,  with  the  complete  guide 
as  to  power  furnished  by  our  tables,  it  is  safe  to  select  engines  properly  proportioned  for  the 
work  they  are  expected  to  perform.  For  ordinary  practice  we  recommend  that  the  selection  be 
made  by  the  following  table : 


T 


B 


SHOWING 


RECOMMENDED  SIZES  OF  ENGINES  FOE  GIVEN  HORSE  POWERS. 


SIZES  OP 

NET 

SIZES  OF 

SIZES  OK 

NET 

SIZES  OF 

LONG  STROKE  ENGINES 

HORSE 

SHORT  STROKE  EXCISES 

LONG  STROKE  ENGINES 

HORSE 

SHORT  STROKE  ENGINES 

DIAMETER            STROKE 

POWER 

DIAMETER              STROKE 

DIAMETER              STROKE 

POWER 

DIAMETER             STROKE 

Inches                   Inches 

Inches                 Inches 

Inches                  Inches 

Inches                  Inches 

5x12 

5 

5x    9 

16x42 

»O 

16x24 

6x16 

1O 

6x    9 

17  x  42 

too 

17x30 

7x20 

15 

7x12 

19x48 

1  ••*.-» 

19x30 

8x20 

9O 

8x12 

21x48 

i.-.o 

21  x  30 

9x24 

93 

9x15 

23x54 

175 

23x36 

10x24 

3O 

10x15 

24  x  54 

•JOO 

24x36 

11x30 

40 

11x18 

26x54 

335 

26x42 

12x30 

50 

12x18 

27x60 

35O 

27  x  42 

13x36 

60 

13x21 

28  x  60 

275 

28x48 

14x36 

70 

14x21 

30x60 

:too 

30x48 

15x36 

80 

15x24 

28        Sizes    of 


Engines 


Recommended    for    Given    3?owers. 


The  engines  in  the  foregoing  table  are  of  sufficient  size  to  furnish  the  net  horse  powers  named 
when  using  80  ft>s.  of  steam,  cut  oft'  at  one-fourth  of  the  stroke ;  and  the  same  power  may  be  obtained 
in  "the  same  engine,  with  greater  economy,  by  increasing  the  steam  pressure  and  shortening  the  point 
of  cut-oft',  and  with  less  economy  by  reducing  the  steam  pressure  and  following  farther  in  the  stroke. 
In  cases  when  there  is  any  uncertainty  as  to  the  amount  of  power  that  will  be  required,  or  when  it  is 
desired  to  have  an  engine  that  will  do  its  work  with  very  little  attention,  it  is  best  to  select  for  the 
given  power  an  engine  one  size  larger  than  is  set  opposite  that  power  in  the  above  table. 


1 


.     •  ' 

HE  tables  on  page  7,  el  seq.,  giving  dimensions,  &c.,  of  the  engines  which  will  furnish  a  desired 
'horse  power,  state  in  columns  G  and  G  the  number  of  pounds  of  water  required  to  be  evaporated 

to  produce  that  horse  power.  That  evaporation  can  be  provided  by  boilers  of  various  kinds  and 
proportion  of  parts.  Local  and  other  considerations  often  decide  the  kind  of  boiler.  In,  order,  therefore, 
to  afford  the  opportunity  of  selecting  the  boiler  that  shall  be  of  adequate  evaporative  power,  and  be  of 
the  kind  preferred,  a  table  is  given  at  the  close  of  this  article,  of  the  four  kinds  of  boilers  most  generally 
in  use;  giving,  for  various  dimensions  of  each  kind,  the  evaporative  capacity  of  each  boiler. 

In  this  table  the  proportion  of  parts  are  those  most  generally  in  use,  which  are  not  always  those 
that  will  give  the  greatest  evaporation  per  pound  of  coal.  Thus  a  cylinder  boiler  18  inches  in  diameter 
and  18  feet  long  will  evaporate  about  7  ft>s.  of  water  per  pound  of  coal,  but  if  made  36  feet  long  it  will 
evaporate  fully  8  Sbs.  per  pound  of  coal. 

The  amount  of  water  evaporated  per  pound  of  coal  under  favorable  conditions  by  each  of  the 
three  kinds  of  boilers  when  proportioned  as  in  our  table,  has  been  ascertained  by  car*eful  experiment 
and  is  given  below : 


NAME  OF  BOILER. 


Water  evaporatea  per  pound  of 
Coal,  at  80  IDS.  pressure,  from 
temperature  of  160°. 

Lbs. 


RELATIVE  EVAPORATION. 


Plain  Cylinder  Boiler, 
Cylinder  Flue 

"        Tubular  " 


6.91 
7.91 
9.15 


1.00 
1.14 
1.32 


The  performance  of  a  locomotive  or  marine  tubular  boiler  is  substantially  the  same  as  that  of  the 
cylinder  tubular,  when  similarly  proportioned. 

In  preparing  the  table  of  evaporative  capacities  of  boilers,  an  allowance  ot  over  25  per  cent,  has 
been  made  to  provide  for  differences  of  management,  draft  and  fuel  which  may  be  met  with. 

The  headings  of  the  columns  in  the  table  show  what  are  the  particulars  stated. 

It  will  be  seen  that  columns  10  and  11  show  the  number  of  pounds  of  water  evaporated,  in  one 
case  from  60°  temperature,  and  in  the  other  from  160°. 

In  cases  where  a  single  boiler  of  dimensions  stated  will  not  furnish  the  evaporation  required, 
modifications  in  number  and  length  will  be  necessary  to  produce  the  required  evaporation. 


8O  Boilers. 


For  example,  if  a  person  select  for  100  horse  power,  an  engine  17  inches  diameter,  42  inches 
stroke,  to  run  at  57  revolutions  per  minute,  and  use  80  pounds  of  steam  cut  oft'  at  £,  the  total  quantity 
of  water  required  per  hour  would  equal  3,488  flbs.  No  single  boiler  in  the  list  will  evaporate  this 
quantity,  but  it  may  be  obtained  by  using 

2  Cylinder  Tubular  Boilers  of  55  inches  diameter,  or 

O  u  U  U  .1*7  .  it  it 

2  Flue  56       " 

g  «  u  u  4.4.          «  <(  it 

4  Plain  Cylinder  36       " 

5  "  "  "  33       '•  " 

As  a  general  rule  it  is  true  economy  to  select  a  boiler  a  little  larger  than  is  required.  The 
variations  from  the  table  in  either  direction  should  not  amount  to  more  than  10  per  cent.  The  amount 
of  water  evaporated  by  either  of  the  plain  cylinder  boilers  may  be  varied,  within  large  limits,  by  altering 
the  length  of  the  boiler.  If  the  grate  surface  and  height  of  bridge  walls  be  proportionately  altered  the 
economy  will  not  be  sensibly  influenced.  The  cylinder  flue  and  cylinder  tubular  boilers  may  be 
shortened  to  reduce  the  heating  surface,  and  will  evaporate  a  quantity  of  water  fully  proportioned  to  the 
reduced  length,  but  at  a  small  sacrifice  of  economy. 


TABLES 

SHOWING    THE    PRINCIPAL   DIMENSIONS    OF    THE 

High  PPSBPMP®  Steam  Boltera 

BUILT  AT 

THE  NOVELTY  IRON  WORKS,  NEW  YORK, 

AND   THE 

Water   Evaporated   per  Hour  by  the  same  from  the  Temperatures  of  60°  and  160°  Fahrenheit. 

KIND 

DIMENSIONS 

•WATER 

Evaporated  per  Hour  at 

O  F1 

SHELL  OF  BOILER 

FLUES  OR  TUBES              STEAM  DRUM 

GRATE 

HEATING 

80  His.    1'ressure  from 

Temperature  of 

BOILER                   DIAMETER        LENGTH 

NUMBER        DIAMETER 

DIAMETER 

HEIGHT 

SURFACE 

SI  RFACE 

60" 

160° 

Inches 

Feet 

Inches 

Inches 

Inches 

Square  Feet 

Square  Feet 

Lbs. 

Lbs. 

18 

18.0 

12 

24 

3.8 

42 

202 

221 

21 

21.0 

14 

28 

5.3 

58 

280 

306 

PLAIN  CYLINDER 

24 

24.0 

15 

30 

6.8 

75 

363 

395 

27 

27.0 

16 

32 

8.6 

95 

458 

501 

BOILERS. 

30 

30.0 

18 

36 

10.7 

118 

569 

622 

33 

33.0 

20 

36 

13.0 

143 

689 

754 

36 

36.0 

20 

40 

15.4 

170 

819 

896 

24 

8.5 

2 

6.5 

12 

24 

3.3 

56 

200 

219 

30 

13.0 

2 

9.0 

15 

30 

6.6 

112 

400 

438 

36 

16.0 

2         ll.o 

18 

30 

9.9 

168 

600 

657 

38 

18.0 

2          12.5 

22 

36 

12.2 

207 

739 

809 

CYLINDER  FLUE 

40 
42 

20.5 
22.0 

2          13.5 
2          14.5 

24 

26 

42 
42 

14.8 
16.9 

252 

288 

900 

1028 

985 
1126 

BOILERS 

44 

23.0            2          15.0 

26 

42 

18.4           313 

1117 

1224 

48 

24.5 

2          16.0 

27 

48 

21.1            359 

1282 

1404 

52 

26.5 

2          17.5 

k   28 

48 

24.9            423 

1500 

1654 

56 

29.0 

2          19.0 

30 

54 

29.5 

501 

1789 

1959 

60 

31.5 

2 

20.5 

32 

54 

34.5 

586 

221)1 

2092 

66 

36.0 

2 

23.0 

36 

60 

43.S 

745 

2660 

2913 

22 

6.5           18 

2.0 

12          24 

2.9 

SO            187 

205 

30 

7.0          22 

2.5 

15 

30 

5.6 

157 

367 

402 

CYLINDER                3(> 

8.5          34 

2.5 

18 

30 

8.2 

229 

536 

586 

40           9.0          42 

2.5 

22 

36 

10.5 

294 

68  S 

753 

TUBULAR                 44 

11.0          40 

3.0 

24 

42 

14.7 

409 

957 

1047 

47 

12.5          34 

3.5 

26 

42 

16.6 

466 

1090 

1193 

BOILERS 

51 

14.0 

34 

4.0 

28 

48 

21.1 

592 

1385 

1516 

55 

14.5 

42 

4.0 

30 

54 

26.5 

742 

1736 

1900 

60 

15.0 

52 

4.0 

34 

54 

33.2 

931 

2178 

2383 

66 

15.0 

60 

4.0 

36 

60 

3S.3 

1072 

2508 

2744 

3.0 

85 

199 

218 

5.9 

165 

386 

422 

LOCOMOTIVE 

8.8 
11.4 

245 
320 

573 
749 

627 
819 

BOILERS. 

14.3 
17.1 

400 
480 

936 
1123 

1024 
1229 

22.5 

630 

1474 

1613 

27.7 

775 

1814 

1984 

1  toilers. 


The  above  boilers  are,  if  desired,  furnished  complete,  with  Cast  Iron  Fronts  and  Doors,  Grate 
Bars  and  Bearers,  Buckstaves  and  Bolts,  Cast  and  Wrought  Iron  Pipe,  Safety,  Feed  and  Stop  Valves, 
Guage  Cocks,  Water  Guages  and  all  other  fixtures  necessary  in  setting  boilers.  Complete  plans  are 
also  furnished  of  the  foundation  and  brickwork. 

For  sizes  and  evaporating  power  of  the  above  boilers,  see  previous  page. 

See  also  the  article  headed  "Boilers,"  on  page  29. 


(The  following  remarks  on  Horse  Power  of  Boilers,  Boiler  Explosions,  &c. ,  are  from  a  paper  read  before  the  Connecticut  Academy  of 

Sciences,  by  W.  P.  TROWBUIDGE.) 


The  term  "  Horse  Power,"  in  its  application  to  boilers,  has  heretofore  been  no  less  indefinite  than  the 
same  term  in  its  application  to  the  engine.  It  has  been  customary  to  fix  upon  some  unit  of  heating  surface 
as  the  unit  of  the  horse  power  of  the  boiler.  The  boiler  is  supposed  to  furnish  a  definite  amount  of  steam  at 
the  working  pressure  employed,  this  amount  depending  on  the  heating  surface ;  and  the  utilization  of  all  this 
steam,  under  the  most  favorable  conditions,  would  thus  furnish,  through  the  medium  of  an  engine,  a  certain 
rate  of  work,  or  a  certain  Horse  Power.  An  inspection  of  the  preceding  tables  of  engines  is  sufficient, 
however,  to  show  that  the  same  quantity  of  water  evaporated  by  a  boiler  will  effect  different  quantities  of 
work  in  the  same  engine,  or  in  different  engines,  under  various  conditions  of  working  ;  these  conditions  being 
the  pressure,  the  degree  of  expansion,  and  the  speed  of  the  piston.  The  rate  of  work  of  the  boiler  thus 
depends  entirely  on  the  engine;  and  the  term  "Horse  Power,"  as  usually  applied,  has  110  very  definite 
signification.  The  effective  power  of  a  given  boiler-apparatus,  including  the  chimney,  or  power  for  producing 
the  draft,  may,  perhaps,  be  estimated  by  supposing  all  the  steam  which  such  a  boiler  can  produce  at  a  given 
pressure,  to  be  utilized  under  the  most  favorable  circumstances  conceivable  in  practice.  But  it  is  still 
apparent  that  the  power  of  the  boiler  is  dependent  upon  the  most  favorable  utilization  of  the  steam. 

A  more  definite  and  positive  mode  of  determining  the  true  theoretical  or  disposable  Horse  Power  of 
boilers  may  be  derived  from  the  investigations  of  Prof.  Zeuner,  Director  of  the  Mining  School  at  Freiberg,  in 
his  work  on  "  The  Mechanical  Theory  of  Heat."  This  new  method  gives  the  maximum  disposable  rate  of  work, 
without  reference  to  the  engine ;  and  hence,  when  an  engine  is  using  all  the  steam  a  boiler  can  produce,  the 
boiler  Horse  Power  may  furnish  a  standard  for  the  economy  of  the  engine. 

The  method  depends  on  the  following  considerations : 

If  we  suppose  the  whole  work  of  the  boiler  to  be  expended  in  producing  a  flow  of  steam  through  a 
small  orifice,  the  velocity  of  the  issuing  steam  is  independent,  of  the  diameter  of  the  orifice,  and  dependent  only 
on  the  pressure ;  but  the  quantity  of  steam  which  flows  through  in  pounds,  will,  of  course,  depend  on  the 
diameter  of  the  orifice ;  and  if  the  size  of  the  orifice  be  just  sufficient  to  allow  all  the  steam  to  escape  which 
the  boiler  can  produce,  the  quantity  which  flows  through  in  pounds,  in  each  second,  will  be  just  equal  to  the 
amount  which  the  boiler  will  produce  in  a  second.  The  work  of  the  boiler  each  second  will  be  expended  in 
imparting  to  this  quantity  of  water,  or  steam,  the  velocity  with  which  it  issues  from  the  orifice,  and  will 
be  equal  to  the  LIVING  FORCE  of  the  mass  in  motion  with  the  issuing  velocity. 

If  M  be  the  quantity  of  water  evaporated  in  pounds,  V  the  issuing  velocity  in  feet  per  second,  this 

living  force  will  be 

V2 
M^r 


The  work  expended  to  produce  the  velocity  V,  in  the  mass  M,  may  be  represented  by  a  constant  force 

V2 
acting  through  a  given  height,  P  h  =  M-^ ;  P.  h.  being  represented  in  foot  pounds.     For  the  work 

V2 
performed  by  the  boiler  in  one  minute  we  have  60  x  P.  h.  =  60  M.  ^        and  if  we  represent  by  M1  the 

weight  of  water,  in  pounds,  evaporated  and  forced  out  of  the  orifice  in  one  minute,  we  have  M1  =  60  M. 

and  60,  P.  h.  =  M1-^— 

60.  P             M1  V2 
If  we  suppose  h  to  be  one  foot,  and  divide  by  33.000,  we  have   oo  QQQ  =  H go  QQQ  =  N,  =  the 

number  of  horse  power  of  the  boiler. 


34:                                           Horse  3?owers  of  Boilers. 

Prof.  Zeuner  furnishes  a  table  of  values  of  the  velocity  V,  in  metre 
from  2  atmospheres,  to  14  atmospheres,  which  is  given  below. 
The  velocities  V,  for  different  pressures,  taken  from  Zeuner's  table, 

For  2  atmospheres  V  —  481 

3  per  second,  for  different  pressures, 
are  as  follows  : 

71  metres  per  second. 

57       "            " 
48       "            " 
33       «             « 

39       "            " 
>7      "           " 
)0       "            " 
!3       "             " 

r4     «         " 

50       "             " 
)0       "             " 
59       "            " 
)6       "            " 

L  units,  have  been  deduced,  and  we 
oretical  horse  power  of  any  boiler. 

OF  BOILEES. 

3           "           COG 

4          "           681. 

5          «           734. 

6          "           774. 

7          «           807  i 

8          "           834  { 

9          «           858  i 

10          "           878  ' 

11          "           896  i 

12           "           913.( 

13          "           927.( 

14          "                                                    941  ( 

From  this  table  the  correspo 
have  the  very  simple  results  in  the 

TABLE  FOE 

V2 

nding  values  °f   3  „  33  QQQ  *n  Englisl 
following  table  for  finding  the  total  the 

FINDING  THE  IIOESE  POWEES 

Pressure  in  Boiler, 
in 
Lbs.  per  Squave  Inch. 

Horse  Power  =  the 
numbers  of  this 
table  multiplied  by  M1 
water  evaporated 
per  minute,  in  Ibs. 

Pressure  in  Boiler, 
in 
Lbs.  per  Square  Inch. 

Horse  Power  =  the 
numbers  of  this 
table  multiplied  by  M1 
water  evaporated 
per  minute. 

14.7 
20 
25 
30 
35 
40 
45 
50 
55 
60 
65 
70 
75 
80 
85 
90 
95 
100 
105 

O.OxM1 
0.5 
0.9 
1.60 
1.45 
1.65 
1.85 
2.05 
2.23 
2.35 
2.52 
2.65 
2.82 
2.87 
3.00 
3.09 
3.19 
3.28 
3.37xM' 

110 
115 
120 
125 
130 
135 
140 
145 
150 
155 
160 
165 
170 
175 
180 
185 
190 
195 
200 

3.43xM' 
3.52 
3.59 
3.65 
3.72 
3.79 
3.85 
3.92 
3.97 
4.02 
4.06 
4.12 
4.18 
4.23 
4.27 
4.32 
4.36 
4.39 
4.40xM' 

To  use  this  table,  find  the  weight  of  water  evaporated  in  each  minute  by  the  boiler,  in  pounds,  and 
multiply  the  number  expressing  this  weight  by  the  number  in  the  table  corresponding  to  the  pressure  in  the 
boiler  ;  the  product  will  be  the  total  disposable  power  of  the  boiler. 

Horse    3?owers    of  Boilers. 


35 


This  new  expression  for  the  disposable  power  of  boilers  was  deduced  incidentally  by  Prof.  Zeuner  as  the 
disposable  power  of  the  steam  after  it  enters  the  cylinder  of  the  engine,  and  he  found  its  equivalent  in  an 
expression  previously  determined  for  the  living  force  of  the  steam  issuing  at  a  high  velocity  into  the 
atmosphere  through  a  small  orifice. 

The  value  of  this  rule  consists  in  the  facility  with  which  it  may  be  employed,  its  absolute  correctness, 
and  the  readiness  with  which  the  performance  of  an  engine  which  utilizes  all  the  steam  produced  by  a  given 
boiler  may  be  compared  with  a  perfect  working  engine,  the  standard  being  from  50  to  60  per  cent,  of  the  horse 
power  of  the  boiler.  A  higher  efficiency  than  60  per  cent,  cannot  probably  be  looked  for  in  practice  with  a 
high-pressure  engine,  as  at  present  constructed.  A  perfect  working  engine  may  also,  conversely,  be  an 
approximate  test  for  the  economic  performance  of  a  given  boiler. 

According  to  determinations  of  Prof.  Zeuner,  based  exclusively  on  the  dynamic  theory  of  heat  applied  to 
the  problem  of  the  efficiency  of  ordinary  high-pressure  engines,  the  utmost  efficiency  possible,  under  the  most 
favorable  conditions  of  expansion,  is  from  50  to  60  per  cent,  of  this  theoretical  power ;  the  40  to  50  per  cent, 
loss  being  inherent  in  the  nature  of  the  engine,  which  no  improvement  can  greatly  alter. 

The  following  test  of  this  theoretical  law,  and  of  the  new  rule  for  the  disposable  power  of  boilers,  is 
derived  from  the  preceding  tables  of  engines.  Taking,  for  comparison,  engines  working  under  steam  at  80 
pounds  pressure,  cutting  off  at  J  of  the  stroke,  and  making  60  revolutions  a  minute,  we  find  for  engines  of 
10,  20,  30,  40,  &c.,  horse  powers  the  quantity  of  water  required  per  minute  from  the  tables,  which  are  based 
on  actual  experiments.  These  quantities  are  introduced  in  the  following  table  in  the  first  column ;  the 
second  column  showing  the  disposable  horse  powers  of  the  boilers  which  produce  exactly  those  quantities  of 
steam ;  the  third  column  shows  the  actual  horse  powers  corresponding  for  the  steam  which  enters  the  cylinder, 
according  to  Mr.  Emery's  experiments.  The  efficiency  of  the  smaller  engines  is  placed  at  53  per  cent.,  and 
of  the  larger  at  60  per  cent.,  the  intermediate  powers  ranging  from  53  to  60. 

If  in  each  case  we  have  a  boiler  which  will  evaporate  just  the  quantity  of  water  given  in  the  first 
column,  we  may  find  the  theoretical  disposable  power  of  these  boilers  by  the  preceding  rule  of  horse  powers 
of  boilers,  which  should  correspond  with  the  results  of  experiments. 

The  results  are  given  in  column  four  of  the  table,  showing  a  remarkable  coincidence.  The  accuracy 
of  the  experimental  results  in  the  steam  engine  tables,  and  the  correctness  of  the  theoretical  laws,  thus  confirm 
each  other. 

These  examples  have  been  taken  at  random.  A  more  extended  and  thorough  comparison  might  be 
made  for  engines  working  under  various  degrees  of  expansion. 

TABLE  OP  COMPARISON. 


Pounds  of  water  which  Total  disposable  power 

Actual  H.  Power  by  in 

T  h.GorGticn.1 

passes  through  cylinder 
of  Engine  = 
Pounds  of  water 
evaporated  by  Boiler 
per  hour. 

of  Steam  at  80  Ibs. 
pressure. 
N  =  horse  power  from 
Table  =  Disposable 
power  of  Steam. 

dicator,  from  Tables  of 
Engines 
Using  amounts  of  water 
in  first  column  with  80 
Ibs.  p.  cutting  off  at  i. 

disposable  power 
of  the  same  steam 
after  it  enters 
the  cylinder. 

400 

19.3  II.  P. 

10 

=  10DiYW,53=    19.0  II.P. 

771 

37.3     " 

20 

20     "     ,53=  36.4 

1159 

56.0     " 

30 

30     "     ,53=  54.5 

1460 

70.1    " 

40 

40     "     ,53=  70.8 

1790 

86.5     « 

50 

50     "     ,56=  87.7 

2136 

103.2     " 

60 

60     "     ,56=102.5 

2469 

119.3     " 

70 

70    «    ,56=117.4 

2790 

134.9     « 

80 

80     "     ,56  =  133.7 

3113 

150.5     " 

90 

90     "     ,56  =  148.7 

3424 

165.5     " 

100 

100     "     ,60  =  166.6 

FEOM  BOILER  POWER. 


FROM  EXPERIMENTAL  ENGINE. 


36 


Horse  Ir'owers  of  Boilers. 


M 
W 


3 


OS     3 
O 


O 


O 

cu 
w 

C/3 

« 

O 

8 


t 


a 


I 

i 


5f 
« 


/ 

-c 


Horse    [Powers    of  Boilers. 


37 


EXPLANATION  OF  THE  DIAGKAM  OF  HOUSE  POWER  OF  BOILERS. 

This  diagram  is  constructed  from  the  table  for  finding  the  horse  powers  of  boilers,  or  from  the  formula 

V 

N=: —          —  the  velocities  being  taken  from  Zeuner's  table  and  reduced  to  English  units. 


2.g.  33. 000. 


The  formula  shows  that  the  curve  which  indicates  the  powers  of  the  same  boiler  with  increasing  pressures 
of  steam,  is  a  common  parabola.  In  the  diagram  the  same  boiler  may  be  supposed  to  be  used  with  steam  press 
ure  increased  according  to  the  numbers  along  the  line  of  abscissas ;  and  supposing  the  same  quantity  of  steam 
M1  to  be  evaporated  each  minute,  which  will  be  approximately  true,  the  ordinatcs  of  the  curve  show  the 
increase  of  disposable  power  of  the  boiler,  as  the  pressure  is  increased. 

The  curve  of  boiler  horse-power,  curve  (1),  supposes  the  evaporation  constant,  under  different  pressures, 
and  exhibits  the  law  of  increase  of  disposal  power  as  the  pressure  rises.  An  increase  of  power  would  also 
attend  increased  evaporation. 

The  quantity  of  water  or  steam  in  pounds  required  for  a  theoretically  perfect  engine,  that  is,  an  engine 
which,  for  instance,  would  utilize  all  the  disposable  work  of  a  boiler,  is  given  by  Prof.  Zeuner  in  the  following 
table,  taken  from  his  work,  the  numbers  being  reduced  to  English  units. 

QUANTITY  OF  VAPOR  EXPRESSED  IN  POUNDS  REQUIRED  IN  A  THEORETICALLY  PERFECT  ENGINE  TO  PRODUCE  ONE 

HORSE  POWER  PER   HOUR. 


Tension  of  the 

Pounds  of  Water  for 

Vapor 
in  Atmosphere. 

One  horse  power 
per  hour. 

1* 

72.9 

3 

32.8 

4. 

26.3 

5 

22.9 

6 

20.7 

8 

18.0 

10 

16.5 

Putting  these  numbers  in  the  form  of  a  curve,  they  are  represented  by  curve  (2)  of  the  preceding  diagram. 

This  curve  exhibits  to  the  eye  the  rate  of  diminution  of  the  quantity  of  steam  required  in  a  perfect 
engine  to  produce  one  horse  power  per  hour  under  the  different  pressures  given  on  the  line  of  abscissas. 

The  lower  curve  (2)  may  be  taken  to  represent,  in  a  general  way,  the  diminution  of  the  size  of  the 
boiler  required  for  a  perfect  engine,  as  the  pressure  rises.  And  the  two  curves  taken  together  show  the 
fallacy  of  estimating  the  horse  power  of  the  boiler  by  heating  surface  alone,  or  without  reference  to  quantity 
of  water  evaporated,  pressure,  &c. 

The  efficiency  of  real  engines  may  be  found,  in  a  general  way,  from  curve  (2),  or  by  the  table  from 
which  it  is  derived,  by  taking  double  the  quantities  of  water  as  the  amount  required  for  any  given  pressure, 
when  the  steam  is  utilized  under  the  most  favorable  conditions. 

THE  EVAPORATIVE  POWER  OF  BOILERS. 

The  quantity  of  water  evaporated  by  a  given  boiler  in  an  hour,  depends  not  only  on  the  heating-surface 
and  the  proportions  of  the  grate-surface,  heating-surface,  and  draft  area,  but  also  upon  the  quantity  of  air 
which  passes  through  the  furnace  in  a  given  time.  A  locomotive  boiler,  for  instance,  burning  ten  pounds  of 
coal  on  each  square  foot  of  grate-surface  in  an  hour,  will  evaporate  about  nine  pounds  of  water  for  each  pound 
of  coal,  under  the  most  favorable  conditions.  The  same  boiler,  running  at  high  speed  and  burning  seventy- 
five  pounds  of  coal  on  each  square  foot  of  grate-surface,  will  evaporate  seven  pounds  of  water  for  each  pound 
of  coal  burned.  The  total  quantity  evaporated  in  an  hour  in  the  first  case  will  be  10x9  =  90  pounds  of  water 
for  each  square  foot  of  grate  surface ;  and  in  the  second  case,  the  same  boiler,  under  a  forced  draft,  will 
evaporate  75  x7=525  of  water  in  one  hour.  Here  there  is  a  vast  difference  in  the  total  amount  of  evapora- 


38  Boiler    Explosions. 


tion ;  but  each  pound  of  coal,  under  the  forced  draft,  produces  less  steam,  in  the  proportion  of  7  to  9  pounds ; 
so  that  while  the  economy  of  fuel  in  one  sense  is  less,  the  total  amount  of  work  done  by  the  same  boiler  in  the 
same  time  is  very  much  greater  with  the  higher  rate  of  combustion. 

The  same  differences  occur  in  stationary  boilers  having  the  same  general  proportions,  but  different 
heights  of  chimneys.  The  chimney  is  the  machine  or  agency  which  produces  the  flow  of  air  through  the  fur 
nace,  and  which,  by  its  height,  determines  the  quantity  which  passes  through  in  a  given  time.  It  is,  therefore* 
the  principal  element  in  the  determination  of  the  total  evaporation  of  a  boiler  in  a  given  time. 

There  are  probably  no  phenomena  connected  with  the  generation  and  utilization  of  steam  so  imperfectly 
defined,  either  theoretically  or  practically,  at  present,  as  those  connected  with  the  quantity  of  air  which  passes 
through  the  furnaces  of  boilers,  under  varying  conditions  of  draft,  and  the  temperatures  of  the  furnace  and 
flues  which  depend  on  this  quantity.  And  hence,  for  greatly  varying  heights  of  chimneys,  the  quantity  of 
coal  consumed  per  hour  can  only  be  determined  in  advance  by  the  most  uncertain  estimates.  It  has  been 
generally  assumed  from  the  experiments  of  Prof.  Johnston,  Mr.  Hunt,  and  others,  that  in  ordinal1}' 
practice  double  the  amount  of  air  necessary  for  complete  combustion  passes  through  the  furnace.  It 
is  contended,  on  the  other  hand,  by  Rankine  and  Clarke,  that  for  high  rates  of  combustion  this  law  is 
not  true ;  and  experiments  made  at  the  Paris  Exposition,  in  which  the  quantity  of  air  was  measured,  in  differ 
ent  cases,  show  that  in  ordinary  practice  this  law  of  double  the  quantity  is  by  no  means  to  be  relied  on. 
Hence  all  attempts  to  reduce  the  laws  of  evaporation  of  boilers  to  fixed  and  definite  rules  of  practice  for  all 
conditions  of  draft,  have  thus  far  been  based  on  assumptions  which  have  no  definite  and  precise  foundation 
in  practice. 

For  stationary  and  steamship  boilers  the  chimneys  are  generally  of  a  uniform  height,  arising  from  the 
nature  of  the  structures  with  which  they  are  connected,  and  hence  the  approximate  amount  of  combustion  on 
a  square  foot  of  grate-surface,  and  the  resulting  evaporation  of  water  per  hour,  are  pretty  well  known  from 
practical  observations.  The  tables  of  evaporation  given  on  page  31  have  been  determined  from  such  consid 
erations,  and  are  not  intended  to  represent  what  the  boilers  there  given  might  accomplish,  under  various  rates 
of  combustion  arising  from  greatly  varying  heights  of  chimneys. 

Experiments  are  greatly  needed  to  determine  the  rates  of  combustion  for  varying  dimensions  of 
chimneys,  as  well  as  the  quantities  of  air  actually  drawn  through  the  furnaces  under  these  varying  rates  of 
combustion.  Such  determinations  are  necessary  in  order  to  establish  the  corresponding  temperatures  of  the 
furnaces  and  the  gaseous  products  of  combustion,  and  from  these,  the  laws  of  transfer  of  heat  by  radiation 
and  contact  in  the  furnaces  and  flues  respectively. 


The  risk  of  life  and  property  involved  in  the  use  of  the  Steam  Boiler  is  still,  as  it  has  always  been,  a 
source  of  constant  anxiety  to  the  Engineer  and  to  the  public.  Explosions  continually  take  place  under 
circumstances  of  the  utmost  apparent  security.  Occurring  without  warning,  and  occupying  but  an  instant  of 
time,  it  is  generally  difficult,  if  not  impossible,  except  in  rare  instances,  to  ascertain  with  certainty  their  true 
cause.  There  is  seldom  a  unanimous  opinion  on  the  part  of  experts  who  examine  into  the  causes  after  the  event. 

The  following  remarks  on  the  subject  are  intended,  therefore,  to  point  out,  as  far  as  possible,  some  of 
the  obvious  sources  of  danger,  which  are  clearly  indicated  by  the  developments  of  the  Dynamic  theory  of 
heat,  and  confirmed  by  actual  experiments.  The  results  will  serve,  perhaps,  to  indicate  more  clearly  the 
direction  in  which  further  experiments  are  needed. 

Explosion  can  occur  from  two  causes  only — first,  from  deficiency  of  strength  in  the  shell  or  other  parts 
of  a  boiler.  This  deficiency  of  strength  may  be  an  original  defect  arising  in  the  material  or  workmanship  at 
the  time  of  construction;  or  it  may  be  due  to  deterioration  from  use,  from  ordinary  wear,  or  from  injuries 
occurring  from  mismanagement,  want  of  attention  and  repairs,  etc.  Manufacturers  and  Engineers  are 
supposed  to  comprehend  fully  these  causes  of  danger,  and  ought  to  be  able  to  avoid  them. 


Boiler    Explosions.  39 


The  other  source  of  danger  arises  from  an  accumulation  of  pressure  within  the  boiler,  to  a  dangerous 
degree  above  that  which  the  structure  is  designed  to  resist.  This  accumulation  of  pressure  may  be  gradual, 
and  due  simply  to  the  increase  of  pressure  which  attends  a  continued  evaporation  when  there  is  not  sufficient 
outlet  for  the  steam  constantly  formed.  This  source  of  danger  will  first  be  discussed. 

One  question  to  be  solved  is  at  what  rate,  in  time,  will  the  pressure  in  any  given  boiler  in  active  use 
increase  if  there  is  no  outlet  for  the  steam.  In  other  words,  how  long  a  time  must  elapse  before  the  pressure 
under  such  circumstances  will  rise  from  an  ordinary  working  pressure  to  a  dangerous  or  prohibited  pressure. 
This  is  a  practical  question,  and  its  solution  ought  to  point  out  the  degree  of  watchfulness  necessary 
on  the  part  of  an  engineer.  It  has  been  solved  in  a  very  thorough  and  practical  manner  by  Mr.  Zeuner,  in 
the  work  to  which  reference  has  been  made. 

The  formula  which  is  given  below  is  Prof.  Zeuner's  formula  derived,  not  from  experiments,  but  in  an 
incidental  manner  from  a  mathematical  discussion  of  the  laws  of  temperature,  pressure,  and  volumes  of 
vapors,  based  on  Regnault's  experiments. 
Let 

T   be  the  time  in  minutes  which  must  elapse  from  the  instant  that  all  egress  of  steam  is  prevented 
in  a  boiler  (by  the  stopping  of  the  engine  and  closing  of  the  safety-valve)  to  the  instant  when  a 
dangerous  or  bursting  pressure  must  follow  in  the  boiler. 
\V    Represent  the  weight  of  water  in  the  boiler. 

t,.  The  temperature  of  the  water  due  to  the  dangerous  pressure. 
t.  The  temperature  due  to  the  working  pressure. 

Q    The  quantity  of  heat  in  units  of  heat  transferred  to  the  water  per  minute. 
Then 

T      -  W  ft"1) 

Q 

the  mean  specific  heat  of  water  being  taken  as  unity. 

This  formula  shows  that  the  time,  T,  is  greater  the  greater  the  amount  of  water  in  the  boiler,  and  it 
diminishes  as  Q  increases.  T  is  less  also  as  (t,  —  t)  is  less.  At  high  pressures  a  greater  change  of  pressure 
accompanies  a  small  change  of  (t,  —  t),  and  T  will  fluctuate  more  rapidly  at  high  pressures  than  at  low 

pressures. 

The  following  examples,  as  illustrations,  will  exhibit  the  applications  of  the  formula  :  — 

EXAMPLE    1. 

A  Marine  Tubular  Boiler  of  the  Largest  Size. 

W=  79,000  Ibs.  of  water. 

Suppose  the  working  pressure  to  be  2£  atmospheres,  and  the  dangerous  pressure  4.  atmospheres, 

(t,  —  1)=29°  Fahr. 

The  boiler  contains  5,000  square  feet  of  heating  surface,  and  supposing  the  evaporation  to  be  2.5  Ibs. 
per  hour  for  each  square  foot  of  heating  surface,  we  have, 

f  5,000  x  .2.5 

Q,  in  pounds  or  water  per  minute  --  .-2-  —  —  --  . 

And  taking  as  a  sufficient  approximation  1,000  units  of  heat  as  the  equivalent  of  the  evaporation  of 

1  Ib.  of  water,  we  have, 

.t      ,  ,  5,000  x  .2.5.  x  1,000 

Q  in  units  or  heat   =  - 

oO. 

These  numbers  introduced  into  the  formula  give, 


T=  =11  minutes. 

5,000  x  .2.5.  x  1,000 

60 
Hence  the  steam  would  reach  a  dangerous  pressure  in  11  minutes. 


4:0  Boiler  Explosions. 


EXAMPLE    2. 

A  Eeturn  Tubular  Boiler,  containing  3,000  Ibs.  of  water,  and  having  500  square  feet  of  heating 
surface,  each  square  foot  evaporating,  as  before,  2£  Ibs.  of  water. 

Suppose  the  ordinary  working  .  pressure  to  be  75  Ibs.,  and  the  dangerous  pressure  to  be  150  Ibs.  per 
square  inch. 

The  formula  gives, 

T=7  minutes. 

EXAMPLE    3. 

A  Locomotive  Boiler,  containing  5,000  Ibs.  of  water,  and  having  11  square  feet  of  grate  surface,  and 
burning  100  Ibs.  of  coal  on  each  square  foot  of  grate  an  hour.  Each  pound  of  c6al  will,  under  such 
conditions,  evaporate  about  7  Ibs.  of  water. 

Suppose  the  working  pressure  to  be  100  Ibs.,  and  the  dangerous  pressure  to  be  200  Ibs.  per  square  inch. 
The  transition  from  the  working  to  the  dangerous  pressure  will  occur  in 

T=2  minutes. 

This  example  is,  of  course,  an  impossible  case,  because  no  locomotive  standing  still  can  burn  100  Ibs. 
of  coal  on  a  square  foot  of  grate  in  an  hour.  It  illustrates,  nevertheless,  the  degree  of  danger  under 
circumstances  which  may  occur.  For  if  we  suppose  this  locomotive  standing  still  to  burn  only  10  Ibs.  of  coal 
per  hour  on  each  square  foot  of  grate,  the  time  T  will  be  increased  ten  times,  and  we  will  have, 

T=20  minutes. 

EXAMPLE  4. 

The  Steam  Fire  Engine.  Taking  an  actual  case.  The  boiler  contains  338  pounds  of  water,  and 
it  has  157  square  feet  of  heating  surface. 

Supposing  each  square  foot  of  heating  surface  to  generate  1  pound  of  steam  in  one  hour,  the  pressure 
will  rise  from  100  to  200  pounds  in 

T=7  minutes. 

EXAMPLE  5. 

To  find  in  the  same  boiler  how  long  a  time  will  be  required  to  get  up  steam.  That  is  to  run  the 
pressure  from  0  to  100  Ibs. 

If  we  suppose  only  1^  cubic  feot  of  water  to  be  introduced  into  the  boiler  at  first,  we  shall  have 

93  x  117 
T  =  157_xlOO<)  =4.1  minutes. 

60 

This  result  is  realized  in  practice,  and  exhibits  the  truth  of  the  formula. 

The  formula  shows  generally  that  boilers  which  contain  large  quantities  of  water  and  burn  coal  slowly, 
have  less  rapid  fluctuations  of  pressure.  And  also  that  the  lowering  of  the  water  in  the  boiler  from  failure  of 
the  feed  apparatus,  by  diminishing  "W,  diminishes  also  T  in  the  same  proportion. 

Low  water  increases  the  danger  of  explosions,  therefore,  not  only  by  exposing  plates  to  overheating, 

W 

followed  by  a  sudden  evolution  of  steam,  but  by  diminishing  the  ratio  — -.     It  is  even  probable  that  Q  is  largely 

Q 

increased  in  such  cases  by  internal  radiation  of  heat  from  the  plates  to  the  water. 

SAFETY  VALVES. 

It  is  supposed  that  a  gradually  increasing  pressure  can  never  take  place  if  the  safety  valve  is  in 
good  working  order,  and  if  it  have  proper  proportions.  Upon  this  assumption,  universally  acquiesced  in,  when 
there  is  no  accountable  cause,  explosions  are  attributed  to  the  "sticking"  of  the  valves,  or  to  "bent  valve 
stems,"  or  "  inoperative  "  valve  springs.  As  the  safety  valve  is  the  sole  reliance  in  case  of  neglect  or  inatten 
tion  on  the  nart  of  the  en.fnne  driver,  it  is  imDortant  to  examine  its  mode  of  working  closelv. 


JBoiler  Explosions. 


41 


It  is  designed  on  the  assumption  that  it  will  rise  from  its  seat  under  the  statical  pressure  in  the  boiler, 
when  this  pressure  exceeds  the  exterior  pressure  on  the  valve,  and  that  it  will  remain  off  its  seat  sufficiently  far 
to  permit  all  the  steam  which  the  boiler  can  produce  to  escape  around  the  edges  of  the  valve. 

The  problem  to  be  solved  is,  then,  to  find  first  what  amount  of  free  orifice  is  necessary  for  the  flow  of 
steam  from  a  given  boiler  under  a  given  pressure,  and  then  to  ascertain  whether  ordinary  valves  will  rise  far 
enough  to  give  this  amount  of  free  orifice. 

The  ordinary  safety  valve,  as  at  present  constructed,  consists  of  a  disc  which  closes  the  outlet  of  a  short 
pipe  leading  from  the  boiler.  The  area  of  the  disc  or  diameter  of  the  valve  is  usually  determined  from  theoretical 
considerations  based  on  the  velocity  of  the  flow,  or  upon  the  results  of  experiments  made  to  ascertain  the  area 
of  orifice  necessary  for  the  flow  of  all  the  steam  a  boiler  can  produce  under  a  given  pressure.  The  fact  is 
recognized  by  engineers  and  constructors,  that  the  real  diameters  of  safety  valves  must  be  greater  than  the 
theoretical  orifices,  because  common  observation  shows  that  the  valves  do  not  rise  appreciably  from  their  seats ; 
and  to  make  the  outlet  around  the  edges  of  the  valve  equal  in  area  to  the  pipe,  the  valve  should  rise  i  of  its 
diameter. 

The  uncertainty  begins  when  it  is  attempted  to  fix  upon  a  diameter.  The  difficulties  of  the  problem 
become  evident  iii  the  light  of  late  experiments. 

In  regard  to  the  area  of  orifice  necessary,  this  question  is  solved  by  Prof.  Zeuner  in  a  very  simple  manner 
theoretically ;  the  following  table  gives  the  results  of  his  determinations  reduced  to  English  units. 

Let  d  be  the  diameter  of  the  orifice  in  inches,  and  w  the  weight  of  steam  which  flows  through  the 
orifice  in  a  second  (equal  to  the  weight  of  water  evaparated  in  a  second)  in  the  problem  under  consideration ; 
then  the  diameters  d  for  different  pressures  are  found  from  the  following  table. 


For  2  atmospheres  d  =  1.72 

3  "  d  —  1.51 

4  "  d  =  IAI 

5  "  d  — 1.35 

6  "  d  =  1.30 

7  "  d  =  1.28 

8  "  d  =  1.22 


For    9  atmospheres  d  =  1.22 
10  d  =  1.21 


12 
13 
14 


d=I.l$ 
d  =  1.18 

d=:1.17 
" 


d  =  1.16 


Boiler  Explosions. 


The  following  Table  gives  the  results  of  experiments  made  at  the  Novelty  Iron  Works  in  New  York 
City,  several  years  before  Prof.  Zeuner's  work  was  published.  These  experimental  results  have  never  before 
been  published.  The  observations  were  made  with  great  care,  with  a  tubular  boiler  adapted  to  the 
experiments. 

The  first  column  gives  the  pressure  in  pounds  per  square  inch  in  the  boiler,  and  the  second  the  area  of 
orifice  in  square  inches  for  each  square  foot  of  heating  surface  of  the  boiler. 


Pressure  in  the  Boiler  in  Area  of  Orifice  in  square 


pounds   above  the   at 
mosphere. 


0.25 

0.5 

1. 

2. 

3. 

4. 

5. 

10. 

20. 

30. 

40. 

50. 

60. 

70. 

80. 

90. 

100. 

150. 

200. 


inches  for  each  square 
foot  of  heating  surface. 


.022794 
.021164: 
.018515 
.014814 
.012345 
.010582 
.009259 
.005698 
.003221 
.002244 
.001723 
.001398 
.001176 
.001015 
.000892 
.000796 
.000719 
.000481 
.000364 


To  compare  the  results  of  Zeuner's  formula,  which  is  entirely  theoretical,  with  the  results  of  these 
experiments,  we  may  assume  that  each  square  foot  of  heating  surface  of  a  tubular  boiler  will  evaporate 
2.5  pounds  of  water  per  hour  with  ordinary  chimney  draft.  Taking  a  series  of  boilers  of  the  different  heating 
surfaces  named  below,  the  comparison  is  given  for  two  pressures,  3  and  5  atmospheres. 


3  ATMOSPHERES. 

5  ATMOSPHERES. 

HKATINO    SURFACE, 

AREA  OF  ORIFICE  BY 

AREA  OF  ORIFICE  BY 

HEATING     SURFACES 

ARF.A  OF  ORIFICE  BY 

AREA  OF  ORIFICE  BY 

SQUARE     FEET. 

EXPERIMENT. 

FORMULA. 

IN  FEET. 

EXPERIMENT. 

FORMULA. 

SQUARE   INCHES. 

SQUARE  INCHES. 

SQUABE  INCHES. 

KQUAUK   INCHES. 

100 

.089 

.09 

100 

.12 

.12 

200 

.180 

.19 

200 

.24 

.24 

500 

.45 

.48 

500 

.59 

.5!) 

1000 

.89 

.94 

1000 

1.20 

1.18 

2000 

1.78 

1.90 

LOGO 

2.40 

2.37 

5000 

4.46 

4.75 

5000 

6.00 

5.95 

At  five  atmospheres  pressure  the  results  from  the  two  sources  are  almost  identical,  and  at  3  atmospheres 
sufficiently  near  to  make  a  remarkable  coincidence.  The  formula  of  Mr.  Zeuner  is,  however,  preferable  in 
practice,  as  it  takes  account  of  the  weight  of  water  evaporated,  which  depends  on  the  amount  of  fuel  burned 
(height  of  chimney,  <&o.}  and  is  therefore  more  comprehensive. 


Boiler    Explosions.  43 


The  mode  of  determining  the  area  of  free  orifice  necessary'for  the  flow  of  steam  may  thus  be  considered 
theoretically  and  practically  settled. 

The  next  question  for  consideration  is,  how  High  will  any  safety  valve  rise  under  the  influence  of  a  • 
given  pressure  ?  This  question  cannot  be  determined  theoretically,  except  that  it  has  been  demonstrated  by 
Zeuner,  Weisbach,  and  others,  that  as  soon  as  the  flow  of  steam  begins  the  pressure  in  the  plane  of  the  orifice 
rapidly  diminishes,  and  in  fact  ceases  at  a  minute  distance  from  the  orifice,  and  is  also  diminished  within  the 
orifice,  in  the  pipe.  It  has  been  supposed  that  the  force  of  the  issuing  steam  striking  against  the  lower  face 
of  the  valve  may  act  to  keep  it  off  its  seat. 

This  question  has  been  settled  conclusively  by  Mr.  Burg,  of  Vienna,  an  account  of  whose  experiments 
was  published  in  the  proceedings  of  the  Vienna  Academy  of  Sciences  in  1862.  Mr.  Burg  made  careful 
experiments  to  determine  the  actual  rise  of  safety  valves  above  their  seats.  He  found  by  actual  measurements, 
made  by  means  of  apparatus  constructed  for  the  purpose,  that  an  ordinary  four-inch  valve  rises  according  to 
the  laws  stated  below.  For  a  boiler  pressure  of 

Ibs.  Ibs.  Ibs.  Ibs.  Ibs.  Ibs.  Ibs.  Ibs.  Ibs. 

12  20  35  45  50  60  70  80  90 

The  rise  of  the  valve  is,  in  parts  of  an  inch, 

1  1  11  1  1  1  1  1 

36  48  54  65  -        86  86  168  132  168 

Or,  taking  average  valves,  the  rise  for  pressures  from  10  to  40  Ibs.  is  ^  of  an  inch,  from  40  to  70  Ibs.  -g1,,-,  and 
from  70  to  90  Ibs.  -^  of  an  inch. 

These  results  show  that  the  rise  diminishes  rapidly,  as  the  pressure  increases — a  result  winch  is  indicated 
by  theory.  The  very  small  rise  for  pressures  from  70  to  90  Ibs.,  y^-  of  an  inch,  is  remarkable. 

If  now  we  take  a  tubular  boiler  with  500  square  feet  of  heating  surface,  the  free  orifice  necessary  for 
the  flow  of  all  the  steam  the  boiler  can  produce  at  5  atmospheres  pressure  will  be,  according  to  Zeuner's 
Formula,  y5^  of  a  square  inch.  Let  x  be  the  diameter  of  the  valve,  which,  by  rising  -^s  of  an  inch,  shall  give 
this  amount  of  free  orifice.  The  circumference  will  be  approximately  3x,  and  we  must  have  3x.  -j^  =.  .59 
square  inches,  from  which  we  find  the  diameter  of  the  required  valve, 

x  =  23.6  inches. 

This  is  an.  impracticable  size.  If  we  assume  a  size  of  six  inches  diameter  as  suitable,  and  ascertain  how 
high  the  valve  must  rise  to  make  an  annular  opening  around  the  edge  equal  to  .59  of  an  inch,  we  may  let  x 
represent  the  rise  of  t'ie  valve.  The  circumference  will  be,  in  round  numbers,  3  x  6  =  18  inches,  and  we 
will  have  18  x  *  =  .59  square  inches ;  x  =  ^  of  an  inch.  This  amount  of  rise  appears  clearly  impossible 
from  the  results  of  Mr.  Burg  given  above,  as  the  valve  will  rise  under  5  atmospheres  only  T^  of  an  inch. 

These  results  have  been  confirmed  in  another  manner.  Baily,  in  experimenting  with  his  volute  springs, 
found  that,  for  an  ordinary  locomotive,  a  valve  of  13  inches  diameter  was  required,  and  with  this  the  pressure 
in  the  boiler  rose  considerably  above  the  pressure  at  which  the  valve  was  set.  With  ordinary  valves  he  found 
that  there  was  no  relief  of  the  boiler  when  the  fires  were  kept  in  full  blast.  Gooch,  the  English  engineer, 
recommended  three  safety  valves  to  each  locomotive.  And  Mr.  llolley,  in  his  recent  work  on  Railway 
Practice,  recognizing  the  inefficiency  of  the  ordinary  valve,  states  that  he  has  seen  the  pressure  in  a  locomotive 
boiler  rise  to  140  Ibs.,  with  two  valves  blowing  off  at  100  Ibs. 

These  facts  and  expressions  from  practical  engineers  are  sufficient  to  confirm  the  foregoing  deductions. 

Another  series  of  experiments,  made  by  Mr.  Burg,  is  still  more  conclusive,  and  justifies  him  in  the 
statement  that  the  "  most  ineoinprehenxible  delusion  has  existed  in  regard  to  the  efficiency  of  the  valve,  as 
commonly  employed ; "  and  that  it  acts  at  most  only  as  an  alarm,  but  cannot  be  depended  on  as  security  against 
explosions. 

His  final  experiments  were  made  with  a  view  of  determining  the  pressure  in  pounds  per  square  inch 
actually  exerted  upon  the  under  surface  of  the  valve,  with  different  amounts  of  rise  or  lift,  and  were  intended 
to  supplement  the  first  experiments. 


44 


Boiler    Explosions. 


Boiler    Explosions.  45 


He  constructed  an  apparatus  by  which  he  was  enabled  to  remove  weights  from  the  exterior  load  on 
the  valve  at  the  same  time  that  he  measured,  by  the  revolutions  of  a  screw,  very  accurately,  the  corresponding 
rise. 

The  results  are  given  in  the  following  diagrams,  which  have  been  made  from  his  published  records. 
Six  experiments  were  made,  in  which  the  pressure  of  steam  in  the  boiler  was  first  taken  at  10  English  Ibs.; 
then  at  27;  again  at  33,  44,  65,  and  75  Ibs.  The  results  correspond  to  the  numbers  1,  2,  3,  4,  5,  6,  in  the 
diagrams. 

At  the  beginning  of  each  experiment  the  valve  was  loaded  to  resist  the  required  pressure  ii»  the  boiler. 
The  curves  1,  2,  3,  4,  5,  6,  represent  the  rising  of  the  valves,  during  each  series,  as  weights  were  taken  off  the 
the  valve.  The  horizontal  line  of  numbers,  0,  5,  10,  15,  &c.,  gives  the  actual  pressures  on  the  lower  surfaces 
of  the  valve  in  pounds  per  square  inch  for  the  rise  of  valve,  as  shown  by  projecting  the  number  down  to  the 
corresponding  curve. 

Thus,  in  the  first  experiment,  beginning  with  ten  Ibs.  constant  pressure  per  square  inch  in  the  boiler, 
the  rise  (curve  (1)  )  was  zero;  by  removing  weights,  |  Ib.  at  a  time,.the  valve  rose  according  to  curve  (1), 
the  height  from  the  base  line,  0,  0,  0,  being  in  lines,  or  ~x  of  an  inch.  With  a  rise  of  1£  lines,  for  instance, 
the  pressure  on  the  lower  surface  of  the  valve  was  only  5  Ibs.,  and  with  a  rise  of  1.9  lines  (about  2  lines,  or 
J  of  an  inch),  the  pressure  on  the  lower  surface  of  the  valve  was  less  than  1  Ib.  per  square  inch. 

Taking  the  fifth  series  of  experiments,  with  a  constant  boiler  pressure  of  65  Ibs.,  it  is  seen  by  curve  5 
that  a  reduction  of  pressure  to  35  Ibs.  (by  unloading  the  valve),  was  necessary,  in  order  that  the  valve  might 
rise  -j4,,-  lines,  or  ^  of  an  inch. 

In  all  the  experiments  a  rise  of  two  lines,  ^  of  an  inch,  as  shown  by  the  curves,  was  only  accomplished 
by  diminishing  the  load  on  the  valves,  until  the  pressure  on  the  under  surface  was  reduced  to  less  than  7  Ibs. 
per  square  inch. 

These  remarkable  results  show  that  when  a  valve  stands  from  its  seat  the  very  small  distance  of  \  of  an 
inch,  there  is  practically  very  little  sustaining  force  in  the  current  of  outflowing  steam.  They  confirm  the 
former  results  that,  to  obtain  a  rise  of  valve  above  the  minimum  height  of  y^  of  an  inch  for  high  pressures, 
an  increasing  pressure  within  the  boiler  is  not  sufficient.  On  the  contrary,  a  diminution  of  exterior  load  on 
the  valve  is  indispensable. 

These  results  show  conclusively  that  the  ordinary  safety  valve  presents  no  real  security.  If  the  fires 
are  kept  up,  and  no  other  relief  afforded  than  the  self-action  of  the  valve,  the  pressure  on  the  boiler  must 
continue  to  rise,*  and  a  few  minutes  inattention  on  the  part  of  an  engineer  may  result  in  an  explosion.  It  is 
not  necessary  to  such  a  result  that  the  valve  should  "  stick,"  or  that  the  stem  should  "  be  bent,"  for  it  is  proved 
beyond  a  doubt  that  the  higher  the  pressure,  the  less  will  the  valve  rise  ;  and  in  not  rising  it  simply  obeys  the 
action  of  the  forces  exerted  upon  it. 


Explosions  arising  from  Sudden  Evolutions  of  Steam. 

A  gradually  increasing  pressure  to  a  dangerous  degree  would  be  impossible  in  any  boiler,  if  the  safety 
valve  were  what  it  is  supposed  to  be,  viz.,  a  perfect  automatic  means  for  liberating  all  the  steam  which  a  boiler 
may  produce  with  the  fires  in  full  blast,  and  all  other  orifices  for  the  escape  of  steam  closed.  Until  such  a 
safety  valve  shall  have  been  devised  and  adopted  into  general  use,  safety  from  gradually-increasing  pressure 
must  depend  on  the  attention  and  watchfulness  of  the  engineer  alone. 

There  are  supposed  to  be,  however,  occasional  instances  of  sudden  or  violent  evolution  of  steam,  in  such 
quantities  that  no  relief  is  possible  through  the  medium  of  safety  valves,  however  perfect  they  may  be  in  their 
functions. 

*  The  form'jja  "or  diameter  of  orifice  shows  that  the  free  orifice  necessary  for  the  issue  of  steam  diminishes  but  slowly  as  the 
pressure  rises. 


4:6  Boiler  Explosions. 


That  such  occurrence  may  take  place  from  natural  causes,  which  do  not  require  for  their  explanation 
any  extraordinary  hypotheses,  such  as  chemical  decomposition  or  electrical  action,  may  perhaps  be  demon 
strated.  But  there  is  reason  to  believe  that  they  are  exceedingly  rare. 

One  of  these  causes  which  has  received  the  most  general  acceptance,  both  in  theory  and  practice,  is  the 
sudden  flow  of  water  upon  plates  which  have  become  overheated  by  the  accidental  lowering  of  the  water  level 
in  the  boiler.  It  is,  in  fact,  considered  almost  an  axiom  that  very  low  water  will  cause  an  explosion. 

There  is  no  doubt  that  exposure  of  the  upper  surfaces  of  flues,  or  the  crown  of  a  furnace,  to  the  intense 
action  of  heat,  when  there  is  no  water  upon  their  surfaces  to  absorb  or  transfer  this  heat,  is  highly  injurious 
and  destructive  to  the  boiler ;  and  on  this  ground  alone  all  the  devices  for  regulating  or  observing  the  water 
level  are  necessary  and  advisable.  It  is  not  certain,  however,  that  even  in  such  an  extreme  case  of  accident 
or  neglect  as  overheated  plates,  an  explosion  must  ensue  if  there  be  an  efficient  safety  valve. 

If  we  suppose  ten  square  feet  of  the  furnace  or  flues  to  become  heated  to  redness,  say  1,000  degrees 
(a  very  extreme  case),  the  quantity  of  heat  in  units  of  heat  which  would  be  transferred  quite  suddenly  but  not 
necessarily  instantaneously,  to  water  coming  in  contract  with  them  at  the  ordinary  boiler  temperature,  would 
be  found  thus :  10  square  feet  of  iron,  \  of  an  inch  thick,  would  weigh  about  100  Ibs.  The  specific  heat  of 
iron  is  .11 ;  and  if  we  take  300°  as  the  temperature  of  the  steam  of  the  boiler,  the  lowering  of  temperature  of  the 
plates  would  be  1,000°— 300°  =  7<)0°,  and  100x700  x. 11  =  7.700  units  of  heat.  This  amount  is  sufficient  to 
evaporate  about  7.7  Ibs.  of  water. 

If  we  refer  to  any  of  the  examples  of  the  application  of  the  formula, 

T_  M  (t.— t,) 

Q 

we  will  find  that  to  raise  the  pressure  from  an  ordinary  working  pressure  to  a  dangerous  pressure,  a  much 
greater  number  of  units  of  heat  was  required,  6.  The  quantity  of  heat  transferred  to  the  boiler  in  each 
•minute  was,  in  the  examples  given,  as  follows,  respectively : 

EXAMPLE  1, 208,300 

2, 20,830 

3, 123,300 

From  these  examples  it  is  seen  that  the  addition  of  only  7.700  units  of  heat,  either  gradually  or 
suddenly,  would  not  cause  a  dangerous  elevation  of  pressure  in  the  boiler,  under  the  conditions  assumed. 

Notwithstanding,  therefore,  the  overheating  of  plates  is  highly  detrimental,  and  no  doubt  dangerous, 
yet  it  seems  probable  that  this  source  of  danger  of  explosions  belongs  to  the  dangers  from  gradually-increased 
pressure,  and  may  be  avoided  by  perfectly  efficient  safety  valves. 

The  occurrence  of  this  cause  of  danger  can  only  happen  from  the  most  culpable  neglect  or  inattention, 
and  cannot  be  regarded  as  an  unforseen  danger,  since  the  means  of  warning  are  abundant. 

The  principal  cause  of  sudden  evolution  of  steam,  which  finds  an  explanation  in  the  known  properties 
of  water,  and  its  action  under  changes  of  temperature,  is  probably  what  is  called  concussive  ebullition. 
This  is  doubtless  a  real  danger,  and  the  more  so  because  it  is  hidden,  and  gives  no  warning.  How  far  this 
phenomenon  takes  place  in  steam  boilers,  and  produces  explosions,  there  are  no  means  of  knowing.  But  that 
it  is  a  possible  cause,  there  seems  to  be  good  reasons  for  believing. 

It  is  known  from  the  investigations  on  the  boiling  points  of  water,  and  other  fluids,  by  Dufour,  Kopp, 
Donny,  and  others,  that  the  conversion  of  water  into  vapor  at  a  certain  temperature  due  to  the  pressure  is 
dependent  on  other  conditions  besides  the  temperature ;  that  water  may  become  heated,  under  certain  con 
ditions,  to  temperatures  many  degrees  above  the  temperature  due  to  its  boiling  point. 

The  phenomenon  called  "concussive  ebullition"  arises,  according  to  Dnfour,  from  the  principle  that  in 
order  that  a  liquid  may  be  transformed  to  vapor  at  any  temperature,  some  portion  of  the  surface  must  be  freely 
exposed  to  a  space  into  which  the  vapor  may  expand.  This  was  demonstrated  by  suspending  drops  of  water  in 
heated  oil.  The  temperature  of  the  water  was  raised  considerably  above  the  boiling-point  without  the  forma 
tion  of  vapor;  but  if  a  bubble  of  air  or  a  piece  of  porous  substance  was  placed  in  contact  with  the  water,  a 


Boiler  Explosions.  47 


burst  of  vapor  occurred.  Professor  Donny,  of  Ghent,  observed  that  water  thoroughly  deprived  of  air,  and 
sealed  up  in  thin  glass  tubes,  free  from  air,  and  heated  at  one  end  of  the  tube,  could  be  heated  to  280°  F., 
under  atmospheric  pressure.  The  burst  of  vapor,  when  it  took  place,  threw  the  whole  mass  of  water  suddenly 
to  the  other  end  of  the  tube. 

This  phenomenon  of  concussive  ebullition  may  be  produced  in  a  variety  of  ways  in  the  chemical  labor 
atory,  and  accompanies  the  processes  for  the  rectification  of  sulphuric  acid  to  such  an  extent  that  special 
means  are  required  to  avoid  its  evil  effects. 

The  practical  conclusion  to  be  derived  from  these  facts  in  connection  with  the  generation  of  steam  in 
steam  boilers,  is  that  the  water  in  a  boiler  may,  under  some  circumstances — such  as  slow-continued  evaporation 
when  a  boiler  is  at  rest,  or  doing  no  work — be  nearly  deprived  of  air,  and  the  circulation  being  then  feeble, 
portions  of  the  water  in  contact  with  the  plates  may  become  heated  to  a  higher  temperature  than  that  of  the 
mass  of  water  above. 

Under  such  circumstances  the  sudden  starting  of  an  engine,  or  other  cause  of  agitation,  producing  an 
increased  circulation  and  an  agitation  of  the  water,  might  cause  a  sudden  evolution  of  steam  in  such  quantities 
and  with  such  force  as  not  only  to  produce  a  dangerous  and  sudden  elevation  of  pressure,  but  a  violent  con 
cussion,  by  throwing  large  masses  of  water  against  the  sides  of  the  boiler. 

It  was  demonstrated  by  Dufcmr  and  others,  that  the  presence  of  air  in  minute  bubbles  prevented  this 
overheating  of  portions  of  the  water,  and  caused  evaporation  to  go  on  continuously.  When  a  boiler  is  at  work, 
circulation  is  rapid  and  continuous,  and  in  most  cases  feed  water  fully  charged  with  air  continually  enters  the 
boiler ;  and  hence  the  conditions  necessary  to  cause  a  retarded  ebullition  are  rare. 

On  this  subject,  however,  further  experiments  and  investigations  are  especially  needed. 

The  general  conclusions  which  may  be  regarded  as  established  from  experiments,  observations,  and 
practice,  thus  far  seem  to  be  : 

1.  That  the  laws  of  resistance  of  the  parts  of  boilers  to  the  internal  pressure  are  sufficiently  well 
established. 

2.  It  is  of  the  utmost  importance  that  the  materials  employed  should  be  of  the  best  quality  as  regards 
strength  and  durability  ;  and  as  there  are  but  few  manufacturers  of  boiler  plates,  the  inspection  of  materials 
especially  boiler  plate,  should  be  made  by  the  government  at  the  place  of  manufacture,  and  the  inspection 
should  extend  to  the  qualities  of  ores  and  the  process  of  manufacture;  the  required  stamps,  brands,  or 
certificates  being  put  on  or  authorized  by  the  inspector  in  person.     There  is   much   greater   certainty   of 
securing  the  best  materials  by  an  inspection  of  the  process  of  working  and  the  raw  materials  employed,  than 
by  an  inspection  of  plates  after  they  have  been  sent  to  market,  when,  to  all  external  appearances,  good  and 
bad  plates  are  not  easily  distinguished. 

3.  An  inspection  of  the  boiler  during  the  process  of  construction.     It  is  impossible  to  discover  all  the 
defects  of  construction  after  a  boiler  is  made. 

•i.  The  deterioration  of  strength  from  wear  and  tear,  from  sudden  heating  or  cooling  of  parts,  from 
oxidation,  &c.,  gives  rise  to  evils  which  can  only  be  avoided  by  constant  attention  and  repairs. 

5.  The  danger  from  sudden  generation  of  steam  in  large  quantities  artses  probably  from  one  cause, 
retarded  ebullition,  and  is  less  likely  to  occur  when  the  boiler  is  at  work,  receiving  constantly  fresh  supplies 
of  water  charged  mechanically  with  air  in  minute  bubbles.     Any  device  which  should  force  air  in  small 
bubbles  into  a  boiler,  would  probably  prevent  this  source  of  danger. 

6.  The  ordinary  construction  of  the  safety  valve  is  fundamentally  defective,  being  based  on  ideas  in 
regard  to  its  action  which  are  unsound  and  delusive.     A  safety  valve  should  be  adopted  which  is   not 
dependent  for  its  action  on  the  pressure  of  the  steam  at  the  orifice  opened  by  the  valve,  and  through  which 
the  steam  flows,  since  it  is  demonstrated  that  the  pressure  at  this  point  practically  ceases  with  any  considerable 
opening  of  the  orifice. 


Boiler    Explosions. 


A  new  construction  for  safety-valves,  suggested  by  the  foregoing  discussion,  is  exhibited  in  the 
following  cuts. 

To  enable  a  valve  to  rise  from  its  seat  an  appreciable  distance,  it  appears,  from  that  discussion, 
that  either  a  portion  of  the  exterior  load  must  be  removed  from  the  valve  the  moment  it  begins  to  rise, 
or  that  a  continuous  sustaining  force  must  act  on  the  valve  from  beneath,  which  shall  not  be  diminished 
by  the  flow  of  steam  through  the  orifice. 

The  latter  expedient  is  adopted,  and  the  end  accomplished,  by  simply  carrying  down  a  stem  from 
the  valve  into  the  water  of  the  boiler.  The  total  pressure  of  steam  upon  the  lower  end  of  this  stem  (or 
if  it  be  hollow,  as  in  the  figure,  upon  the  upper  interior  end  surface)  will  be  continuously  exerted  upon 
the  valve.  In  the  use  of  the  ordinary  disc  or  conical  face  valve,  it  has  been  shown  that  when  the  valve 
stands  one-sixth  of  an  inch  from  its  seat  the  total  force  (or  statical  pressure  and  impulse  combined)  on  the 
lower  surface  of  the  valve  amounts  in  no  case  to  more  than  five  or  six  pounds  per  square  inch. 

If  a  four-inch  stem  be  carried  down  below  the  water  surface,  with  a  pressure  of  60  Ibs.  per  square 
inch  iii  the  boiler,  the  total  pressure  on  the  lower  end  of  the  stem,  transmitted  to  the  valve,  will  be  over 
750  Ibs. 

This  is  equivalent  to  removing  over  45  Ibs.  per  square  inch  from  the  exterior  load.  With  this 
piessure  on  the  main  surface  the  valve  will  rise  from  its  seat,  and  will  continue  to  rise  as  the  pressure 
increases. 

Fig.   1   represents  a  valve  arranged  for  a  marine  boiler. 


V.  Valve.     T.  Stem  carried  below  the  water.     L.  Valve  lever  extended  into  escape  pipe. 

The  force  applied  to  keep  the  valve  down  is  produced  by  a  number  of  spiral  flat  springs  within  a 
barrel,  adjusted  by  a  worm  and  wheel.  This  valve  can  be  locked,  by  locking  the  hand-wheel  which  turns 
the  worm,  and  the  worm  and  wheel  furnishes  a  simple  means  of  adjustment;  all  other  parts  are  inaccessible, 
and  the  force  acting  on  the  valve  cannot  easily  be  altered  by  unauthorized  persons. 


Boiler  Explosions. 


In  Fig.  2,  an  ordinary  lever  is  applied  with  weights,  and  a  diaphragm  is  acted  upon  by  the  pressure  of 
the  water  in  the  tube  or  stem,  the  diaphragm  being  simply  a  metal  plate  with  circular  corrugations. 


To  calculate  the  size  of  valve  for  a  given  boiler,  it  is  to  be  recollected  that  the  circumference 
determines  the  annular  opening  for  the  efflux  of  steam. 

Having  found  the  area  of  orifice  necessary  by  Zeuner's  formula,  a  diameter  is  to  be  chosen,  which  will 
give  this  opening  for  a  given  rise;  for  instance  one-sixth  of  an  inch.  The  diameter  of  the  stem  should 
be  less  than  this  by  one-half  an  inch  (one-fourth  all  around). 

The  statical  pressure  to  be  applied  to  hold  the  valve  down,  may  be  calculated  in  the  ordinary  manner. 
The  valve  seat  should  be  spherical,  and  the  radius  lever  as  long  as  convenient,  in  order  that  the  valve  stem 
may  rise  and  fall  in  a  true  vertical  line.  The  above  described  construction  is  simple,  inexpensive,  practical, 
and  applicable  to  many  boilers  by  simply  putting  a  stem  to  the  valves  already  in  place. 

Where  the  valves  already  in  place  are  too  far  from  the  water,  or  in  such  a  position  that  a  stem 
cannot  be  readily  extended  to  the  water,  a  short  valve  pipe  may  be  bolted  to  the  boiler. 

The  slight  agitation  of  the  valve  stem,  by  the  currents  in  the  boiler,  will  tend  to  keep  the  valve 
well  fitted  to  its  seat,  and  will  prevent  sticking,  if  there  be  any  such  tendency. 

To  illustrate  the  mode  of  finding  the  dimensions  of  a  valve,  according  to  this  construction,  let  it 
be  required  to  find  a  safety  valve  which  shall  furnish  relief  for  all  the  steam  which  a  tubular  boiler  of 
2,000  square  feet  of  fire  surface  can  generate,  with  all  other  orifices  closed  and  the  fires  kept  in  full 
blast.  Let  the  pressure  of  steam  in  such  a  boiler  be  taken  at  5  atmospheres. 

By  the  table,  page  42,  the  free  orifice  necessary  will  be  2.4  square  inches. 

If  a  valve,  4£  inches  diameter,  be  chosen,  the  circumference  will  be  approximately  14.  inches,  and 

1  2.4          1 

it  will  be  necessary  for  the  valve  to  rise  -rr-  of  an  inch.     14.  x  X  =  2.4  inch,  X  =  ~Tf  =  ~F~  °^  an  mcu 

approximately,  X  being  the  rise. 

The  area  of  the  valve  disc  being  4£  inches,  suppose  a  stem  4  inches  diameter  to  be  carried  down 
below  the  water.  The  pressure  on  the  lower  part  of  the  stem  will  be  found  by  multiplying  its  area  in 
square  inches  by  the  boiler  pressure,  or  4.  x  3.1416.  x  75.  =  939  Ibs. 

This  would  be  equivalent  to  removing  939  Ibs.  from  the  exterior  load,  if  the  valve  were  of  the 
ordinary  kind,  such  as  that  used  in  Burg's  experiments. 


5O  Boiler  Explosions. 


To  this  must  be  added  the  diminution  of  atmospheric  pressure  on  the  upper  surface  of  the  valve, 
which  takes  place  when  the  valve  rises.  When  the  valve  is  seated,  the  atmosphere  presses  upon  the  whole 
surface ;  when  it  rises,  only  so  much  of  this  surface  as  is  represented  by  the  cross  section  of  the  stem, 
is  subject  to  the  unbalanced  pressure  of  the  atmosphere.  With  a  4£  inch  valve  and  4  inch  stem,  the 
additional  virtual  diminution  of  exterior  load  will  be,  from  this  cause,  about  90  Ibs.,  and  the  total  diminution 
may  be  taken  at  1,029  Ibs.,  making  a  virtual  relief  of  pressure  of  64  Ibs.  per  square  inch. 

This  would  leave  an  unbalanced  pressure  from  the  exterior  load  of  11  Ibs.  per  square  inch,  upon 
the  area  of  the  valve. 

A  rise  of  one-sixth  of  an  inch  nearly,  as  shown  by  the  curves,  would  take  place,  and  an  increase 
of  pressure  in  the  boiler  more  than  5  Ibs.  above  this  would  be  impossible  from  ordinary  causes. 

It  would  be  advisable  in  the  case  presented  to  make  the  valve  5  inches  in  diameter,  and  thus  secure 
a  margin  for  excessive  firing. 

This  is  believed  to  be  an  exact  method  of  estimating  the  dimensions  of  valves,  and  one  which  will 
be  borne  out  in  practice.  With  the  construction  proposed,  the  gradual  accumulation  of  pressure,  with  all 
other  orifices  closed  and  the  tiring  kept  up,  should  be  impossible,  and  the  valve  becomes  in  reality  a  SAFETY 
valve. 


14DAV 

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